EP3227541B1 - Flap device for an internal combustion engine - Google Patents

Flap device for an internal combustion engine Download PDF

Info

Publication number
EP3227541B1
EP3227541B1 EP15790044.0A EP15790044A EP3227541B1 EP 3227541 B1 EP3227541 B1 EP 3227541B1 EP 15790044 A EP15790044 A EP 15790044A EP 3227541 B1 EP3227541 B1 EP 3227541B1
Authority
EP
European Patent Office
Prior art keywords
housing
bearing
flow
actuator
shaft
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.)
Active
Application number
EP15790044.0A
Other languages
German (de)
French (fr)
Other versions
EP3227541A1 (en
Inventor
Hans Gerards
Andreas GRAUTEN
Jürgen Michels
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.)
Pierburg GmbH
Original Assignee
Pierburg 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 Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP3227541A1 publication Critical patent/EP3227541A1/en
Application granted granted Critical
Publication of EP3227541B1 publication Critical patent/EP3227541B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/1035—Details of the valve housing
    • F02D9/106—Sealing of the valve shaft in the housing, e.g. details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/53—Systems for actuating EGR valves using electric actuators, e.g. solenoids
    • F02M26/54—Rotary actuators, e.g. step motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/70—Flap valves; Rotary valves; Sliding valves; Resilient valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/72—Housings

Definitions

  • the invention relates to a flap device for an internal combustion engine with a flow housing that delimits a flow duct, a flap body which is rotatably arranged in the flow duct, a shaft on which the flap body is attached, an actuator via which the shaft and the flap body can rotate in the flow duct are, an actuator housing in which the actuator is arranged.
  • flap devices are used, for example, as exhaust gas control valves or exhaust gas recirculation valves in low-pressure or high-pressure exhaust gas circuits or as throttle valves in the intake tract of internal combustion engines and are used to regulate the amount of exhaust gas to be returned to the cylinders or to regulate the pressure in the exhaust gas recirculation duct to reduce the pollutant emissions of the engine or to regulate the amount of air drawn in .
  • valves are exposed to different levels of pollution both in terms of the amount of pollutants and the prevailing temperatures.
  • thermal expansions can occur due to the high thermal load, which can lead to the shaft jamming.
  • simple rotatability must be ensured by providing a reliable support with which misalignment can be avoided.
  • Such a valve with a flow housing separable from the actuator housing is from the DE 10 2009 011 951 A1 known.
  • the two housings are fastened to one another by means of two radially extending screws via a fastening frame that is welded to the flow housing, and the valve shaft is connected to the actuator shaft via a coupling.
  • the flap is fully supported in the flow housing at the two axial ends of the shaft.
  • an exhaust flap device in which a sleeve-shaped sealing means surrounds the shaft of the flap outside the housing, a groove being formed in the sealing means which prevents exhaust gas from penetrating outwards along the shaft. Penetration of splash water from the outside in the direction of the bearings cannot, however, be prevented.
  • DE 10 2010 027 930 A1 a flap element in which a holder is welded to the flow housing, from which two part-circular projections extend in the direction of the actuator and engage in a receptacle of a shielding element which is attached to the actuator housing.
  • a seal to the actuator housing is not disclosed.
  • the object is therefore to provide a flap device for an internal combustion engine which has an actuator housing that can be separated from the flow housing, the ingress of splash water between the flow housing and the actuator housing being reliably prevented so that the bearings are protected from damage.
  • the shaft itself should also not be exposed to any splash water, that is to say it should be completely surrounded by the housing in the area protruding from the flow housing. Nevertheless, a correct axial connection and alignment of the actuator housing to the flow housing in order to maintain low actuating forces and prevent the shaft from jamming should be ensured. Furthermore, as little installation space as possible should be required and the flap device should be able to be manufactured inexpensively.
  • a projection extending in the direction of the actuator housing is formed on the flow housing and a receiving element extending in the direction of the flow housing is formed on the actuator housing and rests radially against the projection of the flow housing, with a circumferential groove is formed, and wherein the projection of the flow housing protrudes into the receiving element of the actuator housing and axially rests against a shoulder-shaped end of the receiving element of the actuator housing with the interposition of a seal, on the one hand a correct axial mounting of the actuator housing on the flow housing is ensured and thus a radial offset that could lead to jamming is reliably avoided, with this connection allowing heat to be dissipated from the valve shaft via the actuator housing and, on the other hand, preventing the groove from being caused by from occurring capillary forces, splash water between the projection and the receiving element and thus between the flow housing and the actuator housing can penetrate into the interior of the flap device and thus to the bearings.
  • the projection and the receiving element are preferably designed in the shape of a hollow cylinder, so that, depending on the installation space, the actuator can be rotated relative to the flow housing. Furthermore, the production of the mutually corresponding surfaces of the projection and the receiving element as well as the groove between them is simplified.
  • the shaft advantageously protrudes into the actuator housing and is supported on one side via a first bearing and a second bearing.
  • This arrangement creates a reliable bearing of the shaft, whereby a bearing on the opposite side of the flow housing can be dispensed with. This significantly simplifies assembly.
  • plain bearings insensitivity to thermal stress or contamination is also achieved.
  • these bearings can provide a good thermal Connection and thus heat dissipation to the actuator housing are ensured.
  • the first bearing is preferably arranged in a first bearing receptacle which is formed on the flow housing and the second bearing is arranged in a second bearing receptacle which is formed on the actuator housing.
  • the one-sided flap mounting also leads to an insensitivity to distortion due to thermal stress.
  • the flap can be connected to the actuator in a simple manner with a continuous shaft, so that the assembly can be carried out inexpensively.
  • An additional bearing of an output shaft of the transmission can be dispensed with.
  • the bearing receptacle of the actuator housing, the bearing receptacle of the flow housing, the receiving element and the projection of the flow housing have a common central axis, so that the connection of the shaft to the actuator in the axial direction takes place directly via the bearing points of the two housings, causing an offset can be excluded.
  • a shoulder is preferably formed in the radially inside of the projection of the flow housing, against which an annular disc rests axially, which is fastened in the projection and axially delimits the bearing seat of the first bearing. This prevents axial displacement of the first bearing in the projection.
  • the actuator housing is fastened to the flow housing via connecting plates fastened to the flow housing by means of screws.
  • the first screw being arranged coaxially to the shaft axis and the second screw being arranged tangentially to the shaft axis
  • an optimal alignment of the two bearings can also be set, since both angles and length offsets can be compensated.
  • the bearing clearances to the shaft can also be minimized, which improves the seal and the bearings have a longer service life.
  • the assembly is simplified by using the connecting plates in which bores are formed for the implementation of the screws, with threaded bores for receiving the screws being formed on the actuator housing.
  • the thread can be integrated into the connecting plates so that through-holes are formed in the actuator housing through which the screws are inserted.
  • a sealing ring which surrounds the shaft, is preferably arranged in the second bearing receptacle axially on the side of the second bearing facing away from the flap body. In this way, penetration of hot exhaust gas into the actuator housing can be reliably prevented.
  • a thrust washer is attached to the shaft and is loaded against the second bearing by means of a compression spring.
  • the thrust washer is firmly attached to the shaft and, together with the spring, ensures the axial position of the shaft and thus the flap in the duct.
  • the thrust washer minimizes an exhaust gas flow along the shaft, so that the thrust washer also provides an improved seal.
  • a flap device for an internal combustion engine is thus created with which the penetration of Splash water into the interior of the housing and to the bearings is reliably prevented in a cost-effective manner.
  • the shaft is also protected from contact with splash water, since it is completely surrounded by the housing in the area outside the flow housing.
  • the flap device can be used in the hot gas area, ensuring that the flap or the shaft can move easily even when there is a heat distortion and a damp environment. Correct alignment of the bearings enables the flap or the shaft to rotate with a low torque. Additional bearings are saved, so that assembly is made easier and costs are reduced.
  • the flap device according to the invention has a flow housing 10 which delimits a flow channel 12.
  • the flap body 14 is fastened on a shaft 16 which protrudes through the flow housing 10 into the flow channel 12.
  • a driven gear 18 is attached to the shaft 16, which is part of a spur gear trained transmission 20 is.
  • This transmission 20 is driven by an electric motor 22 when the electric motor 22 is supplied with current accordingly.
  • a drive pinion 26 is attached to an output shaft 24 of the electric motor 22, which acts as a drive element of the gear 20 so that the rotary movement of the electric motor 22 is transferred to the shaft 16 and thus to the flap body 14 via the gear 20.
  • the electric motor 22 and the gear 20 thus serve as an actuator 28 of the flap device and are arranged in a common actuator housing 30, which consists of a main housing part 32 in which the electric motor 22 and the gear 20 are mounted and a cover 36 closing an actuator interior 34, which is attached to the main housing part 32 of the actuator housing 30 with the interposition of a seal 38.
  • the shaft 16 In order to prevent exhaust gas and splash water from penetrating into the actuator housing 30 and to ensure easy rotatability and positioning of the shaft 16 or the flap body 14 in the flow channel 12, the shaft 16 must be reliably supported axially and radially as well as sealed and a connecting surface between the actuator housing 30 and the flow housing 10 are reliably sealed.
  • a hollow cylindrical projection 40 is formed on the flow housing 10, which extends in the direction of the actuator housing 30 and, according to the invention, a circumferential groove 42 is formed on its outer circumference.
  • the hollow cylindrical projection 40 rests with its outer circumference radially against an inner wall of a hollow cylindrical receiving element 44 of the actuator housing 30, which thus radially surrounds the projection 40 over a defined height, the groove 42 within this section of the receiving element 44 Protrusion 40 is formed.
  • This section of the receiving element 44 surrounding the projection 40 accordingly serves as a receiving opening 46 for the projection 40.
  • the formation of the groove 42 at this position has the result that water splashes from the outside through the gap between the outer wall of the projection 40 and the inner wall of the receiving element 44 could penetrate due to capillary forces.
  • An end 47 of the hollow cylindrical projection 40 protruding axially into the receiving opening 46 of the receiving element 44 of the actuator housing 30 also rests against a shoulder 48 of the receiving element 44 axially delimiting the receiving opening 46 with a seal 50 interposed. Should spray water continue to flow from the outside along the gap between the projection 40 and the receiving element 44 despite the groove 42, this is prevented from further penetration by the seal 50.
  • a hollow cylindrical projection 52 of reduced diameter adjoins the receiving element 44, protruding into the actuator interior 34, so that a second shoulder 54 is formed between the axially extending receiving element 44 and the axially extending hollow cylindrical projection 52.
  • the hollow cylindrical projection 52 has a third shoulder 56 on its inside, from which the projection 52 extends again reduced diameter extends.
  • the output gear 18 is located in the extension of this projection 52, so that the shaft 16 extends out of the flow channel 12 through the hollow cylindrical projection 40 of the flow housing 10 and the projection 52 of the actuator housing 30.
  • the shaft 16 is supported on one side via a first bearing 58 and a second bearing 60.
  • the first bearing 58 is arranged in a first bearing receptacle 62 which is formed in the hollow cylindrical projection 40 axially between the housing wall 64 of the flow housing 10 delimiting the flow channel 12 and a shoulder 66 formed on the inner wall of the projection 40.
  • the second bearing 60 is arranged in a second bearing receptacle 68 which is formed axially between the second shoulder 54 and the third shoulder 56 on the projection 52 of the actuator housing 30.
  • the projections 40, 52, the receiving element 44 as well as the bearings 58, 60 and the bearing receptacles 62, 68 have a common central axis 70, which is at the same time the shaft axis.
  • Both bearings 58, 64 are preferably produced as plain bearings made of carbon-graphite and bear radially against the projections 40, 52 surrounding them. Axial movement of the first bearing 58 is limited on the one hand by the housing wall 64 on the other hand by an annular disc 72 which is fastened inside the projection 40 and rests axially against the shoulder 66 which delimits the bearing seat 62 and from which the projection 40 extends extends into the actuator housing 30 with an enlarged inner diameter.
  • This shoulder 66 and thus the bearing 58 are located in a section of the projection 40 that is not surrounded by the receiving element 44, so that heat can be more easily dissipated to the outside from the bearing 58.
  • the second bearing 60 rests axially on the one hand against the third shoulder 56 on the projection 52 and on the other hand against a thrust washer 76 which is firmly connected to the shaft 16.
  • the axial end of the second bearing 60 facing the flap body 14 protrudes slightly beyond the second shoulder 54, so that the thrust washer 76 is arranged in front of the second shoulder 54 when viewed from the direction of the flow housing 10.
  • the thrust washer 76 it is possible for the thrust washer 76 to be pressed against the second bearing 60 via a torsion and compression spring 78 to axially fix the shaft 16 in position and to form an additional seal that clearly allows an exhaust gas flow along the shaft 16 in the direction of the actuator 28 reduced.
  • This spiral-wound torsion compression spring 78 is arranged in the actuator interior 34, radially surrounding the projection 52 and supporting itself on the bottom of the actuator housing 30 and presses against the output gear 18, which is fixedly arranged on the shaft 16, so that the shaft 16 is also axially in this with it Direction is loaded. Furthermore, the two end legs of the spring 78 grip in a known manner behind projections on the actuator housing 30 and on the output gear 18, which cannot be seen in the figures, that the shaft 16 is pretensioned in one direction at least when rotating from the rest position. Correspondingly, if the electric motor 22 fails, the shaft 16 is rotated into an emergency running position due to the spring force.
  • a sealing ring 79 is arranged surrounding the shaft 16, which axially rests against the third shoulder 56 from the side opposite the bearing 60 and additionally seals the shaft leadthrough in the direction of the actuator interior 34.
  • the actuator housing 30 is prepositioned relative to the flow housing 10 by sliding the Receiving element 44 on the projection 40 of the flow housing 10 and against the stop on the shoulder 48. Furthermore, the two bearing receptacles 62, 68 in the actuator housing 30 and in the flow housing 10 ensure that the shaft 16 is optimal both to the transmission 20 and to the flow channel 12 is arranged.
  • the final attachment of the actuator housing 30 to the flow housing 10 takes place via two perpendicularly aligned screws 80, which are inserted through through bores 86, 88 on the flow housing 10 and screwed into threads of weld nuts that are attached to connecting plates 82, 84.
  • the connection plates 82, 84 are also attached to the flow housing 10 by welding.
  • this fastening is also possible the other way around, in that threaded bores are made in the actuator housing.
  • a flap device is thus created in which the penetration of spray water through a gap between the flow housing and the actuator housing is reliably prevented.
  • the section of the shaft protruding from the flow channel and the bearings of the shaft are completely surrounded by the housing, so that contact with the spray water with the resulting corrosion is reliably prevented.
  • an exact alignment of the bearings with respect to one another is ensured, one of which is arranged in the actuator housing and one in the flow housing. This ensures good positioning of the valve body in the channel and a connection to the actuating shaft.
  • a plurality of grooves can also be made between the receiving element and the projection, these grooves both on the outer wall of the projection and on the inner wall the receiving element can be arranged. It is also conceivable to arrange the receiving element within the projection and correspondingly to form the groove on its inner wall or on the outer wall of the receiving element.
  • the structural design of the housing, the drives or gears used and the channel and flap shapes can also be modified.

Description

Die Erfindung betrifft eine Klappenvorrichtung für eine Verbrennungskraftmaschine mit einem Strömungsgehäuse, das einen Strömungskanal begrenzt, einem Klappenkörper, der drehbar im Strömungskanal angeordnet ist, einer Welle, auf der der Klappenkörper befestigt ist, einem Aktor, über den die Welle und der Klappenkörper im Strömungskanal drehbar sind, einem Aktorgehäuse, in dem der Aktor angeordnet ist.The invention relates to a flap device for an internal combustion engine with a flow housing that delimits a flow duct, a flap body which is rotatably arranged in the flow duct, a shaft on which the flap body is attached, an actuator via which the shaft and the flap body can rotate in the flow duct are, an actuator housing in which the actuator is arranged.

Derartige Klappenvorrichtungen werden beispielsweise als Abgasstauklappen oder Abgasrückführventile in Niederdruck- oder Hochdruckabgaskreisläufen oder als Drosselklappen im Ansaugtrakt von Verbrennungsmotoren eingesetzt und dienen zur Regelung einer zu den Zylindern zurückzuführenden Abgasmenge oder zur Regelung des Drucks im Abgasrückführkanal zur Verringerung der Schadstoffemissionen des Motors oder zur Regelung der angesaugten Luftmenge.Such flap devices are used, for example, as exhaust gas control valves or exhaust gas recirculation valves in low-pressure or high-pressure exhaust gas circuits or as throttle valves in the intake tract of internal combustion engines and are used to regulate the amount of exhaust gas to be returned to the cylinders or to regulate the pressure in the exhaust gas recirculation duct to reduce the pollutant emissions of the engine or to regulate the amount of air drawn in .

Je nach Einbauort sind diese Ventile sowohl bezüglich der anfallenden Schadstoffmenge als auch bezüglich der herrschenden Temperaturen unterschiedlich stark belastet. Insbesondere bei Ventilen, welche im Abgasbereich angeordnet sind, können aufgrund der hohen thermischen Belastung Wärmedehnungen entstehen, die zu einem Verklemmen der Welle führen können. Des Weiteren muss auch bei nicht thermisch belasteten Ventilen, welche lediglich einseitig gelagert werden, eine einfache Drehbarkeit sichergestellt werden, indem eine zuverlässige Lagerung bereitgestellt wird, mit der Fluchtungsfehler vermieden werden. Ein solches Ventil mit einem vom Aktorgehäuse trennbaren Strömungsgehäuse ist aus der DE 10 2009 011 951 A1 bekannt. Die beiden Gehäuse werden über einen Befestigungsrahmen, der mit dem Strömungsgehäuse verschweißt ist, mittels zweier radial verlaufender Schrauben aneinander befestigt und die Klappenwelle über eine Kupplung mit der Welle des Aktors verbunden. Die Lagerung der Klappe erfolgt vollständig im Strömungsgehäuse an den beiden axialen Enden der Welle.Depending on where they are installed, these valves are exposed to different levels of pollution both in terms of the amount of pollutants and the prevailing temperatures. In particular in the case of valves that are arranged in the exhaust gas area, thermal expansions can occur due to the high thermal load, which can lead to the shaft jamming. Furthermore, even in the case of valves which are not thermally stressed and which are only supported on one side, simple rotatability must be ensured by providing a reliable support with which misalignment can be avoided. Such a valve with a flow housing separable from the actuator housing is from the DE 10 2009 011 951 A1 known. The two housings are fastened to one another by means of two radially extending screws via a fastening frame that is welded to the flow housing, and the valve shaft is connected to the actuator shaft via a coupling. The flap is fully supported in the flow housing at the two axial ends of the shaft.

Problematisch bei einer derartigen Ausführung ist jedoch, dass eine korrekte Ausrichtung des Strömungsgehäuses zum Aktorgehäuse zum Erhalt einer korrekten Anbindung des Antriebs bei einer derartigen Ausführung nicht sichergestellt ist. Des Weiteren kann Spritzwasser zwischen den Gehäuseteilen von außen in Richtung der Lager eindringen.The problem with such an embodiment, however, is that correct alignment of the flow housing with respect to the actuator housing in order to obtain a correct connection of the drive is not ensured in such an embodiment. Furthermore, splash water can penetrate between the housing parts from the outside in the direction of the bearings.

Des Weiteren ist aus der DE 10 2010 006 023 A1 eine Abgasklappenvorrichtung bekannt, bei der ein hülsenförmiges Dichtmittel die Welle der Klappe außerhalb des Gehäuses umgibt, wobei im Dichtmittel eine Nut ausgebildet ist, die verhindert, dass Abgas entlang der Welle nach außen dringt. Ein Eindringen von Spritzwasser von außen in Richtung der Lager kann jedoch nicht verhindert werden.Furthermore, from the DE 10 2010 006 023 A1 an exhaust flap device is known in which a sleeve-shaped sealing means surrounds the shaft of the flap outside the housing, a groove being formed in the sealing means which prevents exhaust gas from penetrating outwards along the shaft. Penetration of splash water from the outside in the direction of the bearings cannot, however, be prevented.

Zusätzlich offenbart die DE 10 2010 027 930 A1 ein Klappenelement, bei dem am Strömungsgehäuse ein Halter angeschweißt ist, von dem aus sich zwei teilkreisförmige Vorsprünge in Richtung des Aktors erstrecken und in eine Aufnahme eines Abschirmelementes greifen, welches am Aktorgehäuse befestigt ist. Eine Abdichtung zum Aktorgehäuse wird nicht offenbart.In addition, the DE 10 2010 027 930 A1 a flap element in which a holder is welded to the flow housing, from which two part-circular projections extend in the direction of the actuator and engage in a receptacle of a shielding element which is attached to the actuator housing. A seal to the actuator housing is not disclosed.

In allen bekannten Ausführungen von Abgasklappen und insbesondere bei solchen mit trennbaren Aktor- und Strömungsgehäusen kann im Bereich der Anbindung zwischen dem Strömungsgehäuse und dem Aktorgehäuse Spritzwasser eindringen. Dieses Spritzwasser kondensiert im Bereich der Klappenlager und schädigt diese insbesondere in Zusammenhang mit sich an der Welle absetzenden Abgasbestandteilen, was die Lebensdauer einer derartigen Klappenvorrichtung einschränkt.In all known designs of exhaust flaps and especially those with separable actuator and flow housings, in the area of the connection between the flow housing and the Actuator housing splashed in. This splash water condenses in the area of the flap bearings and damages them, in particular in connection with exhaust gas components that settle on the shaft, which limits the service life of such a flap device.

Es stellt sich daher die Aufgabe, eine Klappenvorrichtung für eine Verbrennungskraftmaschine zur Verfügung zu stellen, welche ein vom Strömungsgehäuse trennbares Aktorgehäuse aufweist, wobei ein Eindringen von Spritzwasser zwischen dem Strömungsgehäuse und dem Aktorgehäuse zuverlässig verhindert werden soll, so dass die Lager vor Schäden geschützt werden. Auch soll die Welle selbst keinem Spritzwasser ausgesetzt sein, also im aus dem Strömungsgehäuse ragenden Bereich vollständig vom Gehäuse umgeben sein. Dennoch soll eine korrekte axiale Anbindung und Ausrichtung des Aktorgehäuses zum Strömungsgehäuse zum Erhalt geringer Stellkräfte und einem Verhindern von Verklemmen der Welle sichergestellt wird. Des Weiteren soll möglichst wenig Bauraum benötigt werden und die Klappenvorrichtung soll kostengünstig hergestellt werden können.The object is therefore to provide a flap device for an internal combustion engine which has an actuator housing that can be separated from the flow housing, the ingress of splash water between the flow housing and the actuator housing being reliably prevented so that the bearings are protected from damage. The shaft itself should also not be exposed to any splash water, that is to say it should be completely surrounded by the housing in the area protruding from the flow housing. Nevertheless, a correct axial connection and alignment of the actuator housing to the flow housing in order to maintain low actuating forces and prevent the shaft from jamming should be ensured. Furthermore, as little installation space as possible should be required and the flap device should be able to be manufactured inexpensively.

Diese Aufgabe wird durch eine Klappenvorrichtung mit den Merkmalen des Hauptanspruchs 1 gelöst.This object is achieved by a flap device with the features of main claim 1.

Dadurch, dass am Strömungsgehäuse ein sich in Richtung des Aktorgehäuses erstreckender Vorsprung ausgebildet ist und am Aktorgehäuse ein sich in Richtung des Strömungsgehäuses erstreckendes Aufnahmeelement ausgebildet ist, welches radial gegen den Vorsprung des Strömungsgehäuses anliegt, wobei zwischen dem Vorsprung des Strömungsgehäuses und dem Aufnahmeelement des Aktorgehäuses eine umlaufende Nut ausgebildet ist, und wobei der Vorsprung des Strömungsgehäuses in das Aufnahmeelement des Aktorgehäuses ragt und axial unter Zwischenlage einer Dichtung gegen ein absatzförmiges Ende des Aufnahmeelementes des Aktorgehäuses anliegt, wird einerseits eine korrekte axiale Aufnahme des Aktorgehäuses am Strömungsgehäuse sichergestellt und somit ein radialer Versatz, der zu einem Verklemmen führen könnte, zuverlässig vermieden, wobei durch diese Anbindung ein Abführen von Wärme von der Klappenwelle über das Aktorgehäuse ermöglicht wird und andererseits durch die Nut verhindert, dass aufgrund von auftretenden Kapillarkräften, Spritzwasser zwischen dem Vorsprung und dem Aufnahmeelement und damit zwischen dem Strömungsgehäuse und dem Aktorgehäuse in das Innere der Klappenvorrichtung und somit zu den Lagern eindringen kann. Hierdurch wird die Lebensdauer einer derartigen Klappenvorrichtung deutlich erhöht. Des Weiteren ist die aus dem Strömungsgehäuse ragende Welle vollständig durch das umliegende Gehäuse geschützt. Zusätzlich wird die Dichtigkeit sowohl bezüglich eindringenden Spritzwassers durch die Dichtung erhöht als auch verhindert, dass Abgas, welches entlang der Welle in Richtung des Aktors dringt, nach außen strömt.Characterized in that a projection extending in the direction of the actuator housing is formed on the flow housing and a receiving element extending in the direction of the flow housing is formed on the actuator housing and rests radially against the projection of the flow housing, with a circumferential groove is formed, and wherein the projection of the flow housing protrudes into the receiving element of the actuator housing and axially rests against a shoulder-shaped end of the receiving element of the actuator housing with the interposition of a seal, on the one hand a correct axial mounting of the actuator housing on the flow housing is ensured and thus a radial offset that could lead to jamming is reliably avoided, with this connection allowing heat to be dissipated from the valve shaft via the actuator housing and, on the other hand, preventing the groove from being caused by from occurring capillary forces, splash water between the projection and the receiving element and thus between the flow housing and the actuator housing can penetrate into the interior of the flap device and thus to the bearings. This significantly increases the service life of such a flap device. Furthermore, the shaft protruding from the flow housing is completely protected by the surrounding housing. In addition, the seal increases the tightness with respect to ingress of spray water and prevents exhaust gas, which penetrates along the shaft in the direction of the actuator, from flowing outwards.

Vorzugsweise sind der Vorsprung und das Aufnahmeelement hohlzylinderförmig ausgebildet, so dass je nach Bauraum der Aktor zum Strömungsgehäuse gedreht werden kann. Des Weiteren wird die Herstellung der zueinander korrespondierenden Flächen des Vorsprungs und des Aufnahmeelementes sowie der zwischenliegenden Nut vereinfacht.The projection and the receiving element are preferably designed in the shape of a hollow cylinder, so that, depending on the installation space, the actuator can be rotated relative to the flow housing. Furthermore, the production of the mutually corresponding surfaces of the projection and the receiving element as well as the groove between them is simplified.

Vorteilhafterweise ragt die Welle in das Aktorgehäuse und ist über ein erstes Lager und ein zweites Lager einseitig gelagert. Durch diese Anordnung wird eine zuverlässige Lagerung der Welle geschaffen, wobei auf eine Lagerung an der entgegengesetzten Seite des Strömungsgehäuses verzichtet werden kann. Hierdurch wird die Montage deutlich vereinfacht. Bei Verwendung von Gleitlagern wird zusätzlich eine Unempfindlichkeit gegen thermische Belastung oder Verunreinigungen erreicht. Des Weiteren kann durch diese Lager eine gute thermische Anbindung und somit Wärmeabfuhr zum Aktorgehäuse sichergestellt werden.The shaft advantageously protrudes into the actuator housing and is supported on one side via a first bearing and a second bearing. This arrangement creates a reliable bearing of the shaft, whereby a bearing on the opposite side of the flow housing can be dispensed with. This significantly simplifies assembly. When using plain bearings, insensitivity to thermal stress or contamination is also achieved. Furthermore, these bearings can provide a good thermal Connection and thus heat dissipation to the actuator housing are ensured.

Vorzugsweise ist das erste Lager in einer ersten Lageraufnahme angeordnet ist, welche am Strömungsgehäuse ausgebildet ist und das zweite Lager in einer zweiten Lageraufnahme angeordnet ist, welche am Aktorgehäuse ausgebildet ist. So wird eine korrekte Ausrichtung der Welle zum Aktor und somit eine Leichtgängigkeit des Getriebes sichergestellt. Die einseitige Klappenlagerung führt dabei auch zu einer Unempfindlichkeit gegen Verzug durch thermische Belastung. Zusätzlich ist die Anbindung der Klappe am Aktor auf einfache Weise mit durchgehender Welle möglich, so dass die Montage kostengünstig durchführbar ist. Auf eine zusätzliche Lagerung einer Ausgangswelle des Getriebes kann verzichtet werden.The first bearing is preferably arranged in a first bearing receptacle which is formed on the flow housing and the second bearing is arranged in a second bearing receptacle which is formed on the actuator housing. This ensures correct alignment of the shaft to the actuator and thus smooth running of the gearbox. The one-sided flap mounting also leads to an insensitivity to distortion due to thermal stress. In addition, the flap can be connected to the actuator in a simple manner with a continuous shaft, so that the assembly can be carried out inexpensively. An additional bearing of an output shaft of the transmission can be dispensed with.

Auch ist es vorteilhaft, wenn die Lageraufnahme des Aktorgehäuse, die Lageraufnahme des Strömungsgehäuses, das Aufnahmeelement und der Vorsprung des Strömungsgehäuses eine gemeinsame Mittelachse aufweisen, so dass die Anbindung der Welle zum Aktor in Axialrichtung direkt über die Lagerstellen der beiden Gehäuse erfolgt, wodurch ein Versatz ausgeschlossen werden kann.It is also advantageous if the bearing receptacle of the actuator housing, the bearing receptacle of the flow housing, the receiving element and the projection of the flow housing have a common central axis, so that the connection of the shaft to the actuator in the axial direction takes place directly via the bearing points of the two housings, causing an offset can be excluded.

Des Weiteren ist vorzugsweise im radial Innern des Vorsprungs des Strömungsgehäuses ein Absatz ausgebildet, gegen den axial eine ringförmige Scheibe anliegt, die im Vorsprung befestigt ist und die Lageraufnahme des ersten Lagers axial begrenzt. So wird eine axiale Verschiebung des ersten Lagers im Vorsprung verhindert.Furthermore, a shoulder is preferably formed in the radially inside of the projection of the flow housing, against which an annular disc rests axially, which is fastened in the projection and axially delimits the bearing seat of the first bearing. This prevents axial displacement of the first bearing in the projection.

In einer bevorzugten Ausbildung der Erfindung ist das Aktorgehäuse am Strömungsgehäuse über am Strömungsgehäuse befestigte Verbindungsplatten mittels Schrauben befestigt. So entsteht eine einstellbare und ausrichtbare Befestigung, so dass der Aktor für verschiedene Klappen genutzt werden kann, ohne die Konstruktion ändern zu müssen. Bei einer Verwendung von zwei Schrauben, wobei die erste Schraube koaxial zur Wellenachse angeordnet ist und die zweite Schraube tangential zur Wellenachse angeordnet ist, kann zusätzlich eine optimale Fluchtung der beiden Lager zueinander eingestellt werden, da sowohl Winkel als auch Längenversätze ausgeglichen werden können.In a preferred embodiment of the invention, the actuator housing is fastened to the flow housing via connecting plates fastened to the flow housing by means of screws. This creates an adjustable and alignable attachment so that the actuator for different flaps can be used without having to change the construction. When using two screws, the first screw being arranged coaxially to the shaft axis and the second screw being arranged tangentially to the shaft axis, an optimal alignment of the two bearings can also be set, since both angles and length offsets can be compensated.

Auch können die Lagerspiele zur Welle minimiert werden, wodurch die Abdichtung verbessert wird und die Lager eine längere Lebensdauer aufweisen. Durch die Verwendung der Verbindungsplatten, in denen Bohrungen zur Durchführung der Schrauben ausgebildet sind, wobei am Aktorgehäuse Gewindebohrungen zur Aufnahme der Schrauben ausgebildet sind, wird die Montage vereinfacht. Alternativ kann das Gewinde in den verbindungsplatten integriert werden, so dass im Aktorgehäuse Durchgangsbohrungen ausgebildet sind, durch die die Schrauben gesteckt werden.The bearing clearances to the shaft can also be minimized, which improves the seal and the bearings have a longer service life. The assembly is simplified by using the connecting plates in which bores are formed for the implementation of the screws, with threaded bores for receiving the screws being formed on the actuator housing. Alternatively, the thread can be integrated into the connecting plates so that through-holes are formed in the actuator housing through which the screws are inserted.

Vorzugsweise ist in der zweiten Lageraufnahme axial an der vom Klappenkörper weg weisenden Seite des zweiten Lagers ein Dichtring angeordnet, der die Welle umgibt. So kann ein Eindringen von heißem Abgas in das Aktorgehäuse zuverlässig vermieden werden.A sealing ring, which surrounds the shaft, is preferably arranged in the second bearing receptacle axially on the side of the second bearing facing away from the flap body. In this way, penetration of hot exhaust gas into the actuator housing can be reliably prevented.

Auch ist es vorteilhaft, wenn auf der Welle eine Anlaufscheibe befestigt ist, welche mittels einer Druckfeder gegen das zweite Lager belastet ist. Die Anlaufscheibe ist fest auf der Welle befestigt und sorgt mit der Feder für eine axiale Positionsfestlegung der Welle und damit der Klappe im Kanal. Zusätzlich wird durch die Anlaufscheibe ein Abgasstrom entlang der Welle minimiert, so dass durch die Anlaufscheibe zusätzlich eine verbesserte Abdichtung erzielt wird.It is also advantageous if a thrust washer is attached to the shaft and is loaded against the second bearing by means of a compression spring. The thrust washer is firmly attached to the shaft and, together with the spring, ensures the axial position of the shaft and thus the flap in the duct. In addition, the thrust washer minimizes an exhaust gas flow along the shaft, so that the thrust washer also provides an improved seal.

Es wird somit eine Klappenvorrichtung für eine Verbrennungskraftmaschine geschaffen, mit der ein Eindringen von Spritzwasser in das Gehäuseinnere und zu den Lagern zuverlässig auf kostengünstige Weise verhindert wird. Auch wird die Welle vor dem Kontakt mit Spritzwasser geschützt, da sie im außerhalb des Strömungsgehäuses liegenden Bereichs vollständig vom Gehäuse umgeben ist. Die Klappenvorrichtung kann im Heißgasbereich eingesetzt werden, wobei eine Leichtgängigkeit der Klappe beziehungsweise der Welle auch bei auftretendem Wärmeverzug und feuchter Umgebung sichergestellt wird. Durch eine korrekte Fluchtung der Lager wird das Drehen der Klappe beziehungsweise der Welle mit geringem Drehmoment ermöglicht. Es werden zusätzliche Lager eingespart, so dass die Montage erleichtert wird und Kosten reduziert werden.A flap device for an internal combustion engine is thus created with which the penetration of Splash water into the interior of the housing and to the bearings is reliably prevented in a cost-effective manner. The shaft is also protected from contact with splash water, since it is completely surrounded by the housing in the area outside the flow housing. The flap device can be used in the hot gas area, ensuring that the flap or the shaft can move easily even when there is a heat distortion and a damp environment. Correct alignment of the bearings enables the flap or the shaft to rotate with a low torque. Additional bearings are saved, so that assembly is made easier and costs are reduced.

Ein Ausführungsbeispiel einer erfindungsgemäßen Klappenvorrichtung ist in den Figuren dargestellt und wird nachfolgend beschrieben.

  • Figur 1 zeigt eine Seitenansicht einer erfindungsgemäßen Klappenvorrichtung in geschnittener Darstellung.
  • Figur 2 zeigt eine im Vergleich zum ersten Ausführungsbeispiel um 90° gedrehte Darstellung der erfindungsgemäßen Klappenvorrichtung in geschnittener Darstellung.
An embodiment of a flap device according to the invention is shown in the figures and is described below.
  • Figure 1 shows a side view of a flap device according to the invention in a sectional illustration.
  • Figure 2 shows a representation of the flap device according to the invention, rotated by 90 ° in comparison to the first exemplary embodiment, in a sectional representation.

Die erfindungsgemäße Klappenvorrichtung weist ein Strömungsgehäuse 10 auf, welches einen Strömungskanal 12 begrenzt. Im Strömungskanal 12 ist ein Klappenkörper 14 angeordnet, über den der Durchströmungsquerschnitt des Strömungskanals 12 geregelt werden kann, indem der Klappenkörper 14 im Strömungskanal 12 gedreht wird.The flap device according to the invention has a flow housing 10 which delimits a flow channel 12. A flap body 14, via which the flow cross section of the flow channel 12 can be regulated by rotating the flap body 14 in the flow channel 12, is arranged in the flow channel 12.

Hierzu ist der Klappenkörper 14 auf einer Welle 16 befestigt, die durch das Strömungsgehäuse 10 in den Strömungskanal 12 ragt. Am zum Klappenkörper 14 gegenüberliegenden Ende ist auf der Welle 16 ein Abtriebszahnrad 18 befestigt, welches Teil eines als Stirnradgetriebe ausgebildeten Getriebes 20 ist. Dieses Getriebe 20 wird über einen Elektromotor 22 bei entsprechender Bestromung des Elektromotors 22 angetrieben. Hierzu ist auf einer Ausgangswelle 24 des Elektromotors 22 ein Antriebsritzel 26 befestigt, welches als Antriebsglied des Getriebes 20 wirkt, so dass die Drehbewegung des Elektromotors 22 untersetzt über das Getriebe 20 auf die Welle 16 und damit auf den Klappenkörper 14 übertragen wird.For this purpose, the flap body 14 is fastened on a shaft 16 which protrudes through the flow housing 10 into the flow channel 12. At the end opposite the flap body 14, a driven gear 18 is attached to the shaft 16, which is part of a spur gear trained transmission 20 is. This transmission 20 is driven by an electric motor 22 when the electric motor 22 is supplied with current accordingly. For this purpose, a drive pinion 26 is attached to an output shaft 24 of the electric motor 22, which acts as a drive element of the gear 20 so that the rotary movement of the electric motor 22 is transferred to the shaft 16 and thus to the flap body 14 via the gear 20.

Der Elektromotor 22 und das Getriebe 20 dienen somit als Aktor 28 der Klappenvorrichtung und sind in einem gemeinsamen Aktorgehäuse 30 angeordnet, welches aus einem Hauptgehäuseteil 32, in dem der Elektromotor 22 sowie das Getriebe 20 montiert sind und einem einen Aktorinnenraum 34 verschließenden Deckel 36 besteht, der unter Zwischenlage einer Dichtung 38 am Hauptgehäuseteil 32 des Aktorgehäuses 30 befestigt ist.The electric motor 22 and the gear 20 thus serve as an actuator 28 of the flap device and are arranged in a common actuator housing 30, which consists of a main housing part 32 in which the electric motor 22 and the gear 20 are mounted and a cover 36 closing an actuator interior 34, which is attached to the main housing part 32 of the actuator housing 30 with the interposition of a seal 38.

Um ein Eindringen von Abgas und von Spritzwasser in das Aktorgehäuse 30 zu verhindern und eine einfache Drehbarkeit und Positionierung der Welle 16 beziehungsweise des Klappenkörpers 14 im Strömungskanal 12 sicher zu stellen, muss die Welle 16 zuverlässig axial und radial gelagert sowie abgedichtet werden und eine Verbindungsfläche zwischen dem Aktorgehäuse 30 und dem Strömungsgehäuse 10 zuverlässig abgedichtet werden.In order to prevent exhaust gas and splash water from penetrating into the actuator housing 30 and to ensure easy rotatability and positioning of the shaft 16 or the flap body 14 in the flow channel 12, the shaft 16 must be reliably supported axially and radially as well as sealed and a connecting surface between the actuator housing 30 and the flow housing 10 are reliably sealed.

Hierzu ist am Strömungsgehäuse 10 ein hohlzylindrischer Vorsprung 40 ausgebildet, der sich in Richtung des Aktorgehäuses 30 erstreckt und an dessen Außenumfang erfindungsgemäß eine umlaufende Nut 42 ausgebildet ist. Der hohlzylindrische Vorsprung 40 liegt mit seinem Außenumfang radial gegen eine Innenwand eines hohlzylindrischen Aufnahmeelementes 44 des Aktorgehäuses 30 an, welches somit den Vorsprung 40 über eine definierte Höhe radial fest umgibt, wobei die Nut 42 innerhalb dieses vom Aufnahmeelement 44 umgebenen Abschnitt des Vorsprungs 40 ausgebildet ist. Dieser den Vorsprung 40 umgebende Abschnitt des Aufnahmeelementes 44 dient entsprechend als Aufnahmeöffnung 46 für den Vorsprung 40. Die Ausbildung der Nut 42 an dieser Position hat zur Folge, dass Spritzwasser von außen durch den Spalt zwischen der Außenwand des Vorsprungs 40 und der Innenwand des Aufnahmeelementes 44 aufgrund von Kapillarkräften eindringen könnte. Diese Kapillarkräfte reißen jedoch im Bereich der Nut 42 ab, wodurch ein weiteres Eindringen von Spritzwasser in den Innenraum zuverlässig vermieden wird. Selbstverständlich wird eine gleiche Wirkung auch mit einer Nut erzielt, die an der Innenwand des Aufnahmeelementes 44 statt an der Außenwand des Vorsprungs 40 ausgebildet ist. Zusätzlich wird der aus dem Strömungsgehäuse ragende Abschnitt der Welle 16 vor direktem Kontakt mit Spritzwasser geschützt, da dieser Abschnitt der Welle 16 vollständig vom Aktorgehäuse 30 und dem Vorsprung 40 umgeben ist.For this purpose, a hollow cylindrical projection 40 is formed on the flow housing 10, which extends in the direction of the actuator housing 30 and, according to the invention, a circumferential groove 42 is formed on its outer circumference. The hollow cylindrical projection 40 rests with its outer circumference radially against an inner wall of a hollow cylindrical receiving element 44 of the actuator housing 30, which thus radially surrounds the projection 40 over a defined height, the groove 42 within this section of the receiving element 44 Protrusion 40 is formed. This section of the receiving element 44 surrounding the projection 40 accordingly serves as a receiving opening 46 for the projection 40. The formation of the groove 42 at this position has the result that water splashes from the outside through the gap between the outer wall of the projection 40 and the inner wall of the receiving element 44 could penetrate due to capillary forces. However, these capillary forces tear off in the area of the groove 42, which reliably prevents further penetration of spray water into the interior. Of course, the same effect is also achieved with a groove which is formed on the inner wall of the receiving element 44 instead of on the outer wall of the projection 40. In addition, the section of the shaft 16 protruding from the flow housing is protected from direct contact with splash water, since this section of the shaft 16 is completely surrounded by the actuator housing 30 and the projection 40.

Ein axial in die Aufnahmeöffnung 46 des Aufnahmeelementes 44 des Aktorgehäuses 30 ragendes Ende 47 des hohlzylindrischen Vorsprungs 40 liegt zudem gegen einen die Aufnahmeöffnung 46 axial begrenzenden Absatz 48 des Aufnahmeelementes 44 unter Zwischenlage einer Dichtung 50 an. Sollte somit trotz der Nut 42 Spritzwasser von außen weiter entlang des Spaltes zwischen dem Vorsprung 40 und dem Aufnahmeelement 44 strömen, so wird dieses durch die Dichtung 50 von einem weiteren Eindringen gehindert.An end 47 of the hollow cylindrical projection 40 protruding axially into the receiving opening 46 of the receiving element 44 of the actuator housing 30 also rests against a shoulder 48 of the receiving element 44 axially delimiting the receiving opening 46 with a seal 50 interposed. Should spray water continue to flow from the outside along the gap between the projection 40 and the receiving element 44 despite the groove 42, this is prevented from further penetration by the seal 50.

An das Aufnahmeelement 44 schließt sich in den Aktorinnenraum 34 ragend ein hohlzylindrischer Vorsprung 52 verkleinerten Durchmessers an, so dass zwischen dem sich axial erstreckenden Aufnahmeelement 44 und dem sich axial erstreckenden hohlzylindrischen Vorsprung 52 ein zweiter Absatz 54 ausgebildet ist. Im weiteren Verlauf des hohlzylindrischen Vorsprungs 52 weist dieser an seiner Innenseite einen dritten Absatz 56 auf, von dem aus sich der Vorsprung 52 mit erneut verkleinertem Durchmesser erstreckt. In Verlängerung dieses Vorsprungs 52 befindet sich das Abtriebszahnrad 18, so dass sich die Welle 16 aus dem Strömungskanal 12 durch den hohlzylindrischen Vorsprung 40 des Strömungsgehäuses 10 und den Vorsprung 52 des Aktorgehäuses 30 erstreckt.A hollow cylindrical projection 52 of reduced diameter adjoins the receiving element 44, protruding into the actuator interior 34, so that a second shoulder 54 is formed between the axially extending receiving element 44 and the axially extending hollow cylindrical projection 52. In the further course of the hollow cylindrical projection 52, it has a third shoulder 56 on its inside, from which the projection 52 extends again reduced diameter extends. The output gear 18 is located in the extension of this projection 52, so that the shaft 16 extends out of the flow channel 12 through the hollow cylindrical projection 40 of the flow housing 10 and the projection 52 of the actuator housing 30.

Die Welle 16 wird über ein erstes Lager 58 und ein zweites Lager 60 einseitig gelagert. Das erste Lager 58 ist in einer ersten Lageraufnahme 62 angeordnet, die im hohlzylindrischen Vorsprung 40 axial zwischen der den Strömungskanal 12 begrenzenden Gehäusewand 64 des Strömungsgehäuses 10 und einem an der Innenwand des Vorsprungs 40 ausgebildeten Absatz 66 ausgebildet ist. Das zweite Lager 60 ist in einer zweiten Lageraufnahme 68 angeordnet, welche axial zwischen dem zweiten Absatz 54 und dem dritten Absatz 56 am Vorsprung 52 des Aktorgehäuses 30 ausgebildet ist. Entsprechend weisen die Vorsprünge 40, 52, das Aufnahmeelement 44 sowie die Lager 58, 60 und die Lageraufnahmen 62, 68 eine gemeinsame Mittelachse 70 auf, die gleichzeitig die Wellenachse ist.The shaft 16 is supported on one side via a first bearing 58 and a second bearing 60. The first bearing 58 is arranged in a first bearing receptacle 62 which is formed in the hollow cylindrical projection 40 axially between the housing wall 64 of the flow housing 10 delimiting the flow channel 12 and a shoulder 66 formed on the inner wall of the projection 40. The second bearing 60 is arranged in a second bearing receptacle 68 which is formed axially between the second shoulder 54 and the third shoulder 56 on the projection 52 of the actuator housing 30. Correspondingly, the projections 40, 52, the receiving element 44 as well as the bearings 58, 60 and the bearing receptacles 62, 68 have a common central axis 70, which is at the same time the shaft axis.

Beide Lager 58, 64 werden bevorzugt als Gleitlager aus Kohle-Graphit hergestellt und liegen radial gegen die sie umgebenden Vorsprünge 40, 52 an. Axial wird eine Bewegung des ersten Lagers 58 einerseits durch die Gehäusewand 64 andererseits durch eine ringförmige Scheibe 72 begrenzt, die im Innern des Vorsprungs 40 befestigt ist und axial gegen den Absatz 66 anliegt, der die Lageraufnahme 62 begrenzt und von dem aus sich der Vorsprung 40 mit vergrößertem Innendurchmesser in das Aktorgehäuse 30 erstreckt. Dieser Absatz 66 und damit das Lager 58 befinden sich in einem Abschnitt des Vorsprungs 40, der nicht vom Aufnahmeelement 44 umgeben ist, so dass Wärme aus dem Lager 58 einfacher nach außen abgeführt werden kann.Both bearings 58, 64 are preferably produced as plain bearings made of carbon-graphite and bear radially against the projections 40, 52 surrounding them. Axial movement of the first bearing 58 is limited on the one hand by the housing wall 64 on the other hand by an annular disc 72 which is fastened inside the projection 40 and rests axially against the shoulder 66 which delimits the bearing seat 62 and from which the projection 40 extends extends into the actuator housing 30 with an enlarged inner diameter. This shoulder 66 and thus the bearing 58 are located in a section of the projection 40 that is not surrounded by the receiving element 44, so that heat can be more easily dissipated to the outside from the bearing 58.

Das zweite Lager 60 liegt axial einerseits gegen den dritten Absatz 56 am Vorsprung 52 und andererseits gegen eine Anlaufscheibe 76 an, die fest mit der Welle 16 verbunden ist. Das zum Klappenkörper 14 weisende axiale Ende des zweiten Lagers 60 ragt geringfügig über den zweiten Absatz 54 hinaus, so dass die Anlaufscheibe 76 aus Richtung des Strömungsgehäuses 10 betrachtet vor dem zweiten Absatz 54 angeordnet ist. Auf diese Weise wird es möglich, dass die Anlaufscheibe 76 über eine Dreh- und Druckfeder 78 zur axialen Lagefixierung der Welle 16 gegen das zweite Lager 60 gedrückt wird und eine zusätzliche Abdichtung bildet, die einen Abgasstrom entlang der Welle 16 in Richtung des Aktors 28 deutlich reduziert.The second bearing 60 rests axially on the one hand against the third shoulder 56 on the projection 52 and on the other hand against a thrust washer 76 which is firmly connected to the shaft 16. The axial end of the second bearing 60 facing the flap body 14 protrudes slightly beyond the second shoulder 54, so that the thrust washer 76 is arranged in front of the second shoulder 54 when viewed from the direction of the flow housing 10. In this way, it is possible for the thrust washer 76 to be pressed against the second bearing 60 via a torsion and compression spring 78 to axially fix the shaft 16 in position and to form an additional seal that clearly allows an exhaust gas flow along the shaft 16 in the direction of the actuator 28 reduced.

Diese spiralförmig gewickelte Dreh-Druckfeder 78 ist im Aktorinnenraum 34, den Vorsprung 52 radial umgebend und sich am Boden des Aktorgehäuses 30 abstützend angeordnet und drückt gegen das fest auf der Welle 16 angeordnete Abtriebszahnrad 18, so dass mit diesem auch die Welle 16 in dieser axialen Richtung belastet wird. Des Weiteren greifen die beiden Endschenkel der Feder 78 in bekannter Weise derart hinter in den Figuren nicht erkennbare Vorsprünge am Aktorgehäuse 30 und am Abtriebszahnrad 18, dass die Welle 16 in eine Richtung zumindest bei Drehung aus der Ruhestellung vorgespannt ist. Entsprechend wird die Welle 16 aufgrund der Federkraft bei Ausfall des Elektromotors 22 in eine Notlaufposition gedreht.This spiral-wound torsion compression spring 78 is arranged in the actuator interior 34, radially surrounding the projection 52 and supporting itself on the bottom of the actuator housing 30 and presses against the output gear 18, which is fixedly arranged on the shaft 16, so that the shaft 16 is also axially in this with it Direction is loaded. Furthermore, the two end legs of the spring 78 grip in a known manner behind projections on the actuator housing 30 and on the output gear 18, which cannot be seen in the figures, that the shaft 16 is pretensioned in one direction at least when rotating from the rest position. Correspondingly, if the electric motor 22 fails, the shaft 16 is rotated into an emergency running position due to the spring force.

Am in den Aktorinnenraum 34 weisenden Ende des Vorsprungs 52 ist die Welle 16 umgebend ein Dichtring 79 angeordnet, der axial von der zum Lager 60 gegenüberliegenden Seite gegen den dritten Absatz 56 anliegt und die Wellendurchführung zusätzlich in Richtung des Aktorinnenraums 34 abdichtet.At the end of the projection 52 pointing into the actuator interior 34, a sealing ring 79 is arranged surrounding the shaft 16, which axially rests against the third shoulder 56 from the side opposite the bearing 60 and additionally seals the shaft leadthrough in the direction of the actuator interior 34.

Bei der Montage erfolgt eine Vorpositionierung des Aktorgehäuses 30 zum Strömungsgehäuse 10 durch das Aufschieben des Aufnahmeelementes 44 auf den Vorsprung 40 des Strömungsgehäuses 10 und gegen den Anschlag am Absatz 48. Des Weiteren wird durch die beiden Lageraufnahmen 62, 68 im Aktorgehäuse 30 und im Strömungsgehäuse 10 sichergestellt, dass die Welle 16 sowohl zum Getriebe 20 als auch zum Strömungskanal 12 optimal angeordnet ist.During assembly, the actuator housing 30 is prepositioned relative to the flow housing 10 by sliding the Receiving element 44 on the projection 40 of the flow housing 10 and against the stop on the shoulder 48. Furthermore, the two bearing receptacles 62, 68 in the actuator housing 30 and in the flow housing 10 ensure that the shaft 16 is optimal both to the transmission 20 and to the flow channel 12 is arranged.

Die endgültige Befestigung des Aktorgehäuses 30 am Strömungsgehäuse 10 erfolgt über zwei senkrecht zueinander ausgerichtete Schrauben 80, die durch Durchgangsbohrungen 86, 88 am Strömungsgehäuse 10 gesteckt und in Gewinde von Schweißmuttern, die an Verbindungsplatten 82, 84, befestigt sind, geschraubt werden. Die Verbindungsplatten 82, 84 sind ebenfalls durch Schweißen am Strömungsgehäuse 10 befestigt. Selbstverständlich ist diese Befestigung auch umgekehrt möglich, indem im Aktorgehäuse Gewindebohrungen eingebracht werden.The final attachment of the actuator housing 30 to the flow housing 10 takes place via two perpendicularly aligned screws 80, which are inserted through through bores 86, 88 on the flow housing 10 and screwed into threads of weld nuts that are attached to connecting plates 82, 84. The connection plates 82, 84 are also attached to the flow housing 10 by welding. Of course, this fastening is also possible the other way around, in that threaded bores are made in the actuator housing.

Es wird somit eine Klappenvorrichtung geschaffen, bei der ein Eindringen vom Spritzwasser durch einen Spalt zwischen dem Strömungsgehäuse und dem Aktorgehäuse zuverlässig verhindert wird. Der aus dem Strömungskanal ragende Abschnitt der Welle und die Lagerungen der Welle sind vollständig vom Gehäuse umgeben, so dass ein Kontakt zum Spritzwasser mit daraus folgender Korrosion zuverlässig verhindert wird. Zusätzlich wird eine exakte Ausrichtung der Lager zueinander sichergestellt, von denen eines im Aktorgehäuse und eines im Strömungsgehäuse angeordnet ist. So werden eine gute Positionierung des Klappenkörpers im Kanal und eine Anbindung der Stellwelle sichergestellt.A flap device is thus created in which the penetration of spray water through a gap between the flow housing and the actuator housing is reliably prevented. The section of the shaft protruding from the flow channel and the bearings of the shaft are completely surrounded by the housing, so that contact with the spray water with the resulting corrosion is reliably prevented. In addition, an exact alignment of the bearings with respect to one another is ensured, one of which is arranged in the actuator housing and one in the flow housing. This ensures good positioning of the valve body in the channel and a connection to the actuating shaft.

Es sollte deutlich sein, dass der Schutzbereich des vorliegenden Hauptanspruchs nicht auf die beschriebenen Ausführungsbeispiele begrenzt ist. Insbesondere können auch mehrere Nuten zwischen dem Aufnahmeelement und dem Vorsprung angebracht werden, wobei diese sowohl an der Außenwand des Vorsprungs als auch an der Innenwand des Aufnahmeelementes angeordnet werden können. Auch ist es denkbar, das Aufnahmeelement innerhalb des Vorsprungs anzuordnen und entsprechend die Nut an dessen Innenwand oder an der Außenwand des Aufnahmeelementes auszubilden. Die konstruktive Ausgestaltung der Gehäuse, die verwendeten Antriebe oder Getriebe sowie die Kanal- und Klappenformen können ebenfalls abgeändert werden.It should be clear that the scope of protection of the present main claim is not limited to the exemplary embodiments described. In particular, a plurality of grooves can also be made between the receiving element and the projection, these grooves both on the outer wall of the projection and on the inner wall the receiving element can be arranged. It is also conceivable to arrange the receiving element within the projection and correspondingly to form the groove on its inner wall or on the outer wall of the receiving element. The structural design of the housing, the drives or gears used and the channel and flap shapes can also be modified.

Claims (9)

  1. Flap device for an internal combustion engine comprising
    a flow housing (10) delimiting a flow duct (12),
    a flap body (14) rotatably arranged in the flow duct (12),
    a shaft (16) on which the flap body (14) is fastened,
    an actuator (28) via which the shaft (16) and the flap body (14) can be rotated in the flow duct (12),
    an actuator housing (30) in which the actuator (28) is arranged,
    wherein a protrusion (40) which extends in the direction of the actuator housing (30) is formed on the flow housing (10) and a receiving element (44) which extends in the direction of the flow housing (10) is formed on the actuator housing (30) and abuts radially on the protrusion (40) of the flow housing (10),
    characterized in that
    a circumferential groove (42) is formed between the protrusion (40) of the flow housing (10) and the receiving element (44) of the actuator housing (30), and wherein the protrusion (40) of the flow housing (10) protrudes into the receiving element (44) of the actuator housing (30) and, with the interposition of a seal (50), abuts axially against a shoulder-shaped end (47) of the receiving element (44) of the actuator housing (30).
  2. Flap device for an internal combustion engine of claim 1, characterized in that the protrusion (40) and the receiving element (44) are formed as a hollow cylinder.
  3. Flap device for an internal combustion engine of one of the preceding claims, characterized in that the shaft (16) protrudes into the actuator housing (30) and is supported on one side by a first bearing (58) and a second bearing (60).
  4. Flap device for an internal combustion engine of claim 3, characterized in that the first bearing (58) is arranged in a first bearing receptacle (62) formed on the flow housing (10) and the second bearing (60) is arranged in a second bearing receptacle (68) formed on the actuator housing (30).
  5. Flap device for an internal combustion engine of claim 4, characterized in that the bearing receptacle (68) of the actuator housing (30), the bearing receptacle (62) of the flow housing (10), the receiving element (44) and the protrusion (40) of the flow housing (10) have a common central axis (70).
  6. Flap device for an internal combustion engine of one of claims 4 or 5, characterized in that a shoulder (66) is formed radially inside of the protrusion (40) of the flow housing (10), against which an annular disc (72) abuts axially, which disc is fastened in the protrusion (40) and axially delimits the bearing seat (62) of the first bearing (58).
  7. Flap device for an internal combustion engine of one of the preceding claims, characterized in that the actuator housing (30) is fixed to the flow housing (10) by means of connecting plates (82, 84) fastened to the flow housing (10) using screws (80).
  8. Flap device for an internal combustion engine of one of claims 4 to 7, characterized in that a sealing ring (79) surrounding the shaft (16) is arranged axially in the second bearing seat (68) on the side of the second bearing (60) averted from the valve body (14).
  9. Flap device for an internal combustion engine of one of claims 3 bis 8, characterized in that a thrust washer (76) is fixed on the shaft (16), which washer is loaded against the second bearing (60) by means of a compression spring (78).
EP15790044.0A 2014-12-02 2015-10-19 Flap device for an internal combustion engine Active EP3227541B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014117675.8A DE102014117675B4 (en) 2014-12-02 2014-12-02 Valve device for an internal combustion engine
PCT/EP2015/074120 WO2016087108A1 (en) 2014-12-02 2015-10-19 Flap device for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP3227541A1 EP3227541A1 (en) 2017-10-11
EP3227541B1 true EP3227541B1 (en) 2021-05-19

Family

ID=54396834

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15790044.0A Active EP3227541B1 (en) 2014-12-02 2015-10-19 Flap device for an internal combustion engine

Country Status (3)

Country Link
EP (1) EP3227541B1 (en)
DE (1) DE102014117675B4 (en)
WO (1) WO2016087108A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017112002A1 (en) 2017-05-31 2018-12-06 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Actuator for an internal combustion engine
DE102018114360B4 (en) * 2018-06-15 2021-03-04 Pierburg Gmbh Flap device for an internal combustion engine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5531205A (en) * 1995-03-31 1996-07-02 Siemens Electric Limited Rotary diesel electric EGR valve
DE102008001834A1 (en) * 2007-05-18 2008-11-20 Denso Corp., Kariya-shi Fluid control valve for combustion engine, has housing with wall surface, which defines fluid passages that are configured and stays in connection with combustion chamber in combustion engine
DE102009011951B4 (en) * 2009-03-10 2013-08-22 Küster Holding GmbH Exhaust flap device for motor vehicles and method for assembling an exhaust valve device
DE102010006023B4 (en) * 2010-01-27 2012-04-26 Pierburg Gmbh Sealing arrangement for a control device of an internal combustion engine
DE102010027930B4 (en) * 2010-04-19 2014-01-09 Faurecia Abgastechnik Gmbh flap element
DE102012103926B4 (en) * 2012-05-04 2015-01-08 Pierburg Gmbh Valve bearing system for a flap shaft in a motor vehicle

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
WO2016087108A1 (en) 2016-06-09
EP3227541A1 (en) 2017-10-11
DE102014117675B4 (en) 2017-10-26
DE102014117675A1 (en) 2016-06-02

Similar Documents

Publication Publication Date Title
EP2961972B1 (en) Flap device for an internal combustion engine
DE102012111810B4 (en) Valve device for an internal combustion engine
DE102013101938B4 (en) Drive arrangement for a unit of an internal combustion engine and exhaust gas recirculation valve
DE102006054041B3 (en) Regulating device for an internal combustion engine
DE102010028982B4 (en) Throttle device
WO2011091909A1 (en) Sealing arrangement for a control device of an internal combustion engine
DE102014104578B4 (en) Flap device for an internal combustion engine
EP3227540B1 (en) Flap device for an internal combustion engine
EP2929165B1 (en) Flap device for an internal combustion engine
EP2881634A1 (en) Flap assembly for an actuator, in particular for an exhaust valve of a combustion engine
DE102014104577A1 (en) Exhaust flap device for an internal combustion engine
DE102018114360B4 (en) Flap device for an internal combustion engine
EP3227541B1 (en) Flap device for an internal combustion engine
DE102009025490A1 (en) Supply line e.g. lubricant supply pipe, for use in internal combustion engine of motor vehicle, has side pieces, where line is displaced from coaxial position of central axis such that central axis and central axis of recess subtend angle
DE102017130323B3 (en) Valve device for an internal combustion engine
EP3126651B1 (en) Flap device for an internal combustion engine
EP2772625B1 (en) Drive assembly for a unit of an internal combustion engine
EP3431735A1 (en) Flap device
EP2795167A1 (en) Valve device
EP2917539B1 (en) Flap device for an internal combustion engine or an electric vehicle
DE102013106627B4 (en) Valve device for an internal combustion engine
DE102017110858A1 (en) Hot gas unit
DE102016204440A1 (en) Adjusting device for an internal combustion engine

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170413

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

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20180309

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20201216

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

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: DE

Ref legal event code: R096

Ref document number: 502015014735

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1394184

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210615

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: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20210519

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

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: 20210519

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: 20210519

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: 20210819

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: 20210519

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

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: 20210919

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: 20210820

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: 20210519

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: 20210519

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: 20210519

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: 20210519

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: 20210819

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: 20210920

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

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: 20210519

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

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: 20210519

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: 20210519

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: 20210519

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: 20210519

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: 20210519

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: 20210519

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: 20210519

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502015014735

Country of ref document: DE

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

26N No opposition filed

Effective date: 20220222

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502015014735

Country of ref document: DE

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: 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: 20210919

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: 20210519

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20211031

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

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: 20210519

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: 20211019

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: 20210519

Ref country code: DE

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

Effective date: 20220503

Ref country code: BE

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

Effective date: 20211031

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: 20211031

Ref country code: CH

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

Effective date: 20211031

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: 20211019

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1394184

Country of ref document: AT

Kind code of ref document: T

Effective date: 20211019

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: 20211019

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

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: 20151019

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: 20210519

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

Ref country code: GB

Payment date: 20231025

Year of fee payment: 9

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

Ref country code: FR

Payment date: 20231023

Year of fee payment: 9