EP3245127B1 - Braking and locking unit for a control-signal generator - Google Patents

Braking and locking unit for a control-signal generator Download PDF

Info

Publication number
EP3245127B1
EP3245127B1 EP16707615.7A EP16707615A EP3245127B1 EP 3245127 B1 EP3245127 B1 EP 3245127B1 EP 16707615 A EP16707615 A EP 16707615A EP 3245127 B1 EP3245127 B1 EP 3245127B1
Authority
EP
European Patent Office
Prior art keywords
braking
locking
spring arms
rotor
inner rotor
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
EP16707615.7A
Other languages
German (de)
French (fr)
Other versions
EP3245127A1 (en
Inventor
Karl-Heinz Schweer
Anja QUAST
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.)
Aventics GmbH
Original Assignee
Aventics 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 Aventics GmbH filed Critical Aventics GmbH
Publication of EP3245127A1 publication Critical patent/EP3245127A1/en
Application granted granted Critical
Publication of EP3245127B1 publication Critical patent/EP3245127B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
    • G05G9/00—Manually-actuated control mechanisms provided with one single controlling member co-operating with two or more controlled members, e.g. selectively, simultaneously
    • G05G9/08—Manually-actuated control mechanisms provided with one single controlling member co-operating with two or more controlled members, e.g. selectively, simultaneously the controlled members being actuated successively by progressive movement of the controlling member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H21/00—Use of propulsion power plant or units on vessels
    • B63H21/21—Control means for engine or transmission, specially adapted for use on marine vessels
    • B63H21/213—Levers or the like for controlling the engine or the transmission, e.g. single hand control levers
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
    • G05G1/00—Controlling members, e.g. knobs or handles; Assemblies or arrangements thereof; Indicating position of controlling members
    • G05G1/08—Controlling members for hand actuation by rotary movement, e.g. hand wheels
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
    • G05G5/00—Means for preventing, limiting or returning the movements of parts of a control mechanism, e.g. locking controlling member
    • G05G5/06—Means for preventing, limiting or returning the movements of parts of a control mechanism, e.g. locking controlling member for holding members in one or a limited number of definite positions only

Definitions

  • the invention relates to a unit for defined rest and braking of a manually operable command transmitter for the speed and transmission adjustment of marine propulsion.
  • the field of application of the present invention extends to ship control technology.
  • the helm of ships is usually equipped with a command transmitter for remote control of the ship propulsion.
  • the commanders acts nowadays usually as an actuator via an electrical connection to an electric motor control of the ship's drive directly controlling the speed and / or transmission adjustment of the ship's drive.
  • Such manually mechanically adjustable command transmitter must be performed sufficiently stable to protect against accidental adjustment by vibration or light touch to remain safe in the selected position. At the same time they should be sensitive and adjustable without noticeable breakaway torque between the switching positions.
  • the actuator engages clearly noticeable at the switching positions of the travel.
  • Typical gearshift positions are, for example, the positions gearbox neutral - gearbox advance - gearbox back on drives with reverse gearboxes, the position Propeller Neutral on drives with variable pitch propellers.
  • DD 244533 A1 From the DD 244533 A1 is a command generator for marine propulsion with a drive lever, a switching disc and a driven by a first hydraulic actuator locking disk, which are mounted on a rotatably mounted shaft known.
  • a locking disk engages a locking pin, which is actuated by a further hydraulic actuator motor.
  • a brake acting on the edge of the locking disc is provided, which is actuated by a third servo motor.
  • the of the DD 244533 A1 proposed locking and braking function is complex due to the required hydraulic actuators, production-consuming and has a high space requirement.
  • a commander of the aforementioned type is known, which is rotatably mounted in addition to its longitudinal axis in both directions of rotation against a spring action and which detects a rotational movement detecting sensor for controlling an aggregate, for example.
  • a motor control having.
  • the addition to the storage of the hand lever regardless of this executed spring damping of the rotary motion requires additional components and has an additional space requirement.
  • a locking device for a machine telegraph in which a command lever with a detent roller is displaceably guided on a detent track.
  • Such a device has depending on the selected height of the locking projections relative to the recesses either a relatively high breakaway torque or a relatively unstable position in the respective switching position. Further, it is advantageous to pivot the command generator on a circular path, rather than linearly displaceable, since this is space-saving in the provision of the same length switching path and allows a more ergonomic operation.
  • the brake element comprises an outer rotor with a bearing shell forming an opening and an inner rotor disposed in the opening, which are rotatably mounted relative to each other, wherein the inner rotor one or more radially against a spring force can be erected, one-sided connected to this braking members, each in a in the lateral surface of the inner rotor introduced recess can be pressed and bear against the inner surface of the bearing shell.
  • the DE 103 52 445 B4 disclosed brake element (so-called Minibremselement) is not suitable for use as a command station due to its spatial dimensions and also provides no manually operated actuator, such as a lever, or means for mounting such an actuator before.
  • the brake element exerts due to the identical orientation of the or the brake elements within the plane of rotation only in one direction - against the Aufstellmoment the brake elements - a braking function or the braking function in the opposite direction is at least significantly reduced.
  • the DE 103 52 445 B4 proposed brake element no means for locking the inner rotor against the outer rotor before.
  • Brake detents are also off US4905537 . FR2359979 . US4646588 or JP2009286165 known.
  • the invention has for its object to provide a storage unit for a manually operated command transmitter with an integrated combined braking / locking function, which is as compact and simple as possible and can be easily and inexpensively manufactured and assembled.
  • the core of the invention is a brake-locking unit for command transmitter with an outer rotor with a bearing ring forming a circular opening and an opening disposed in the inner rotor, which are arranged rotatably relative to each other, one of the two rotor elements statically fixed in position and the other rotor element is formed either with a manually operable actuator or designed with such a connectable and the inner rotor is arranged with at least three radially arranged in the circumferential direction and one side connected to this spring arms, which are each pressed into a recess located in the lateral surface of the inner rotor, wherein at least one Spring arm is formed at its free end with a locking means which releasably positively and non-positively cooperates with at least one corresponding recess in the running surface of the bearing ring and at least two spring arms in pairs inn half of the plane of rotation are arranged in opposite directions and are each formed at their free ends with a braking means and wherein the spring arms via the brake and locking means in
  • the respectively in its position statically fixed rotor element serves as fixed in its position stator (inside or outside stator), for example, by being mounted on or on a console or an elevated housing.
  • the other, in this rotatably mounted rotor element is used to change the switching position by either with a manually operated actuator,
  • a lever is formed or configured with such a connectable by having, for example, holes for screwing a control lever.
  • the spring arms arranged in the circumferential direction with braking means exert different friction moments on the running surface depending on the direction of rotation. This is greater in the direction of rotation against the pitching moment of the respective spring arm than in the opposite direction.
  • the spring arms with braking means in the plane of rotation are arranged in pairs opposite each other in opposite directions, the two friction moments exerted by them add up to an identicalPolreibmoment, whereby the brake / locking unit is braked substantially uniformly stabilizing in both directions.
  • the latching recess (s) in the running surface of the bearing ring each represent the switching position (s) of the brake / latch unit.
  • the brake / locking unit is stabilized in the respective position.
  • the respective spring arm (s) is pressed with latching means in the respective recess in the lateral surface of the inner rotor, wherein the latching means leaves the respective latching recess again.
  • An even greater uniformity of the braking effects exerted in both directions of rotation is achieved by providing at least two spring arms with latching means in a brake-latching unit with a total of at least four spring arms and arranged in pairs opposite each other within the plane of rotation, the latching means being arranged in a common radial section are and in each case in synchronism with the or the recess (s) cooperate.
  • the spring arms with locking means act radially non-positively on the running surface of the bearing ring and thus exert a certain frictional torque against the rotation of the brake / latch unit. This is greater in the direction of rotation against the pitching moment of the respective spring arm than in the opposite direction.
  • the locking means are each a Federarmcrues arranged in a common radial portion and respectively synchronously cooperate with the same recess, at the same time an identical breakaway torque is ensured when releasing the detent in both directions without an additional second recess for each spring arm second locking means must be provided in the running surface of the bearing ring.
  • the locking means of a Federarmcrues within the same radial portion are preferably arranged adjacent to each other in the circumferential direction. This ensures a compact design while maintaining a steady in both directions breakaway torque.
  • the spring arms with brake means and / or the spring arms with latching means are configured spring-loaded, wherein the compression springs are arranged in the inner rotor and act radially on the spring arms.
  • the required for the desired friction torque of the braking means and the sufficiently stable seat of the locking means radial force is generated substantially by the bias of the compression springs.
  • Compression springs can be designed due to the design at a correspondingly predetermined preload and spring force with a much smaller spring rate than is possible with only designed as leaf springs spring arms.
  • the spring force and thus also the radial force exerted by you on the brake and locking means can always be made almost constant even with different component tolerances.
  • the radial forces required for the desired friction torque and the desired stability of the seat of the latching means in the latching recesses - independently of each other - can be varied and adapted to different requirements.
  • the spring arms, locking means and braking means are designed with the inner rotor as a one-piece component.
  • the braking / locking unit consists in this embodiment with all the necessary functional elements only two components.
  • the inner and outer rotor as plastic injection molded parts are executed, the production can be further simplified and costs can be further reduced. Furthermore, this design ensures a very low overall weight of the device.
  • the rotatable rotor element is formed with a sensor magnet. This allows recordable, in cooperation with a corresponding Hall sensor, a non-contact detection of the angular position of the rotatable rotor element and thus also an associated with this actuator.
  • the brake / lock unit according to FIGS. 1 and 2 consists of an outer rotor 1 and an inner rotor 2, which is formed with three spring arms 3, 3 'and 3 "arranged radially in the circumferential direction and fixedly connected to the latter on one side, designed as leaf springs, below the spring arms 3, 3' and 3" in the lateral surface of the inner rotor 2 respectively corresponding recesses into which the spring arms 3, 3 'and 3 "can be pressed in.
  • the spring arms 3 and 3' are at their free end with the braking means 4 and 4 ', the spring arm 3" with the Detent 5 is formed.
  • the spring arms 3, 3 ', 3 ", the brake means 4, 4' and the latching means 5 are designed as a one-piece component with the inner rotor 2.
  • the outer rotor 1 has a circular opening which has a bearing ring with the running surface 6 for receiving the inner rotor
  • the outer rotor 1 is formed with three latching recesses 7, 7 'and 7 ", which serve for the positive reception of the latching means 5 and determine the corresponding switching positions of the brake / latching unit.
  • the spring arms 3, 3 ', 3 " are pressed into the respective corresponding recesses in the lateral surface of the inner rotor 2 and the inner rotor 2 is inserted into the outer rotor 1. Due to the prestressing produced thereby, the spring arms 3, 3', 3" act in the assembled state according to FIG.
  • a frictional torque is generated in particular via the braking means 4 and 4 ', which counteracts a rotational movement of the inner rotor 2 against the outer rotor 1.
  • the bias of the spring arms 3, 3 ' is in this case selected such that they generate the radial force required for the desired friction torque.
  • the two spring arms 3 and 3 'arranged in the circumferential direction exert different friction moments on the running surface 6 via the brake means 4 and 4' depending on the direction of rotation. This is greater in the direction of rotation against the pitching moment of the respective spring arm than in the opposite direction.
  • the two spring arms 3 and 3 'in the plane of rotation are arranged in opposite directions to each other, the two friction moments exerted by them add up in each case to an identicalPolreibmoment, whereby the brake / latch unit is braked substantially uniformly stabilizing in both directions of rotation.
  • the bias of the spring arm 3 is chosen such that a sufficiently stable positive and non-positive fit of the locking means 5 is ensured in the recesses 7, 7 'and 7" in the switching positions at the same time the lowest possible breakaway torque when loosening the seat.
  • the preload is thus chosen so that an unwanted adjustment by vibration while driving or a light touch is sufficiently reliably avoided, but at the same time a sensitive adjustment is made possible without too much effort.
  • the outer rotor 1 serves as a stator by being connected via the radially arranged threaded bore 9 with a housing and is fixed statically in the installed state in its position.
  • the inner rotor 2 is rotatably mounted in the installed state in the outer rotor 2 and is used to manually change the switching position by means of a control lever which can be screwed on the front side bores 10 and 10 'to the inner rotor 2.
  • FIG. 3 shows an alternative, compatible with the outer rotor 1 embodiment of an inner rotor 2 'with two within the rotation plane to each other in opposite directions arranged spring arms 3a and 3b with locking means 5a and 5b.
  • the spring arm 3 "exerts a certain frictional torque on the running surface 6 of the outer rotor 1 via the latching means 5 in the prestressing required for a sufficiently stable positive and non-positive fit in the latching recesses 7, 7 'and 7".
  • This friction torque is greater in the direction of rotation than the setting moment of the spring arm 3 "in the opposite direction 5a and 5b ensure equal friction in both directions of rotation and ensure absolute uniformity of the braking action exerted in both directions of rotation Since the two locking means 5a and 5b are also arranged in a common radial section and cooperate synchronously with the locking recesses 7, 7 'and 7'' , is in this embodiment of the inner rotor 2 'also identical in both directions of rotation Losbrechmoment ensured without additional recesses in the tread 6 must be created.
  • FIGS. 4 and 5 show an alternative embodiment of the brake / latch unit.
  • the outer rotor 1 'and the inner rotor 2 "are designed with an integrated ball bearing and form with the groove elements 11a and 11b a common circumferential groove for balls arranged in it, of which on the sectional view FIG. 4 the truncated balls 12 and 12 'can be seen. Since the bearing is designed as a fully spherical bearing, no separate ball cage is required. The groove is sufficiently deep, so that axial forces can be absorbed. This ensures that one connected to the frontal bores 10 "'and 10""of the inner rotor 2", in the FIGS.
  • a stop element 14a which is connected to the inner rotor 2 "at the end is guided between two stop elements 14b and 14b 'which are connected to the outer rotor 1' by means of the inner rotor 2" whereby the degree of freedom of the rotational movement is guided of the inner rotor 2 "is limited to a total of 140 °.
  • the inner rotor 2" is also provided with a recess 15 for receiving one in the front side FIGS. 4 and 5 provided sensor magnet, not shown. In cooperation with a corresponding, in the FIGS.

Description

Technisches GebietTechnical area

Die Erfindung betrifft eine Einheit zum definierten Rasten und Bremsen eines manuell bedienbaren Kommandogebers für die Drehzahl- und Getriebeverstellung von Schiffsantrieben.The invention relates to a unit for defined rest and braking of a manually operable command transmitter for the speed and transmission adjustment of marine propulsion.

Stand der TechnikState of the art

Das Einsatzgebiet der vorliegenden Erfindung erstreckt sich auf die Schiffssteuerungstechnik. Der Steuerstand von Schiffen ist üblicherweise mit einem Kommandogeber zur Fernsteuerung des Schiffsantriebs ausgerüstet. Der Kommandogeber wirkt hierbei heutzutage in der Regel als Stellglied über eine elektrische Verbindung zu einer elektrischen Motorsteuerung des Schiffsantriebs direkt ansteuernd auf die Drehzahl-und/oder Getriebeverstellung des Schiffsantriebs. Solche manuell mechanisch verstellbaren Kommandogeber müssen zum Schutz vor ungewollter Verstellung durch Vibration oder leichter Berührung hinreichend stabil geführt sein, um sicher in der jeweils gewählten Stellung zu verbleiben. Gleichzeitig sollten sie aber feinfühlig und ohne merkliches Losbrechmoment zwischen den Schaltpositionen verstellbar sein. Zur exakten Steuerung ist es ferner erforderlich, dass das Stellglied an den Schaltpositionen des Stellweges deutlich spürbar einrastet. Typische Schaltpositionen sind bei Antrieben mit Wendegetrieben beispielsweise die Positionen Getriebe Neutral - Getriebe Voraus - Getriebe zurück, bei Antrieben mit Verstellpropellern die Position Propeller Neutral.The field of application of the present invention extends to ship control technology. The helm of ships is usually equipped with a command transmitter for remote control of the ship propulsion. The commanders acts nowadays usually as an actuator via an electrical connection to an electric motor control of the ship's drive directly controlling the speed and / or transmission adjustment of the ship's drive. Such manually mechanically adjustable command transmitter must be performed sufficiently stable to protect against accidental adjustment by vibration or light touch to remain safe in the selected position. At the same time they should be sensitive and adjustable without noticeable breakaway torque between the switching positions. For exact control, it is also necessary that the actuator engages clearly noticeable at the switching positions of the travel. Typical gearshift positions are, for example, the positions gearbox neutral - gearbox advance - gearbox back on drives with reverse gearboxes, the position Propeller Neutral on drives with variable pitch propellers.

Bei allgemein im Stand der Technik bekannten Kommandogebern wird die Rastfunktion häufig über federbelastete Kugeln oder Rollen ausgeführt, die lösbar in eine entsprechende Gegenbohrung oder -nut eingreifen. Für die Bremsfunktion werden zum Beispiel Bandbremsen, die auf eine Welle wirken, oder axial wirkende Bremselemente, die federbelastet auf eine Scheibe wirken, eingesetzt. Nachteilhaft ist bei diesen Lösungen, dass eine Vielzahl von Bauteilen erforderlich ist, die exakt positioniert sein müssen und sich möglichst spielfrei zueinander bewegen müssen. Eine Rastkugel, die nicht exakt in die Kugelpfanne greift oder eine Bremse mit Umkehrspiel sorgen für eine schwammig wirkende Betätigung und vermitteln den Eindruck mangelnder Präzision. Jede dieser Komponenten unterliegt zudem einem Verschleiß, weshalb die Umsetzung der verschiedenen Funktionen mit möglichst wenigen Bauteilen wünschenswert ist. Schließlich ist die Montage vieler kleiner Einzelteile unwirtschaftlich.In generally known in the art commanders the detent function is often performed on spring-loaded balls or rollers that engage releasably in a corresponding counterbore or groove. For example, for the brake function Band brakes that act on a shaft, or axially acting brake elements that act spring loaded on a disc used. A disadvantage of these solutions that a large number of components is required, which must be positioned precisely and move as free of play to each other. A detent ball that does not grasp the ball socket exactly or a brake with backlash creates a spongy acting and give the impression of lack of precision. Each of these components is also subject to wear, which is why the implementation of various functions with as few components is desirable. Finally, the assembly of many small items is uneconomical.

Aus der DD 244533 A1 ist ein Kommandogeber für Schiffsantriebe mit einem Fahrhebel, einer Schaltscheibe und einer durch einem ersten hydraulischen Stellmotor angetriebenen Rastscheibe, die auf einer drehbar gelagerten Welle befestigt sind, bekannt. In die Rastscheibe greift ein Raststift an, der über einen weiteren hydraulischen Stellmotor betätigt wird. Ferner ist eine am Rande der Rastscheibe wirkende Bremse vorgesehen, die durch einen dritten Stellmotor betätigt wird. Die von der DD 244533 A1 vorgeschlagene Rast- und Bremsfunktion ist aufgrund der erforderlichen hydraulischen Stellmotoren komplex, produktionsaufwändig und besitzt einen hohen Raumbedarf.From the DD 244533 A1 is a command generator for marine propulsion with a drive lever, a switching disc and a driven by a first hydraulic actuator locking disk, which are mounted on a rotatably mounted shaft known. In the locking disk engages a locking pin, which is actuated by a further hydraulic actuator motor. Furthermore, a brake acting on the edge of the locking disc is provided, which is actuated by a third servo motor. The of the DD 244533 A1 proposed locking and braking function is complex due to the required hydraulic actuators, production-consuming and has a high space requirement.

Aus der DE 19936946 C1 ist ein Kommandogeber für Schiffsantriebe mit einem in einer Schaltkulisse geführten, in zwei Funktionsebenen schwenkbaren Handhebel bekannt. Zum Einrasten des Schalthebels in seinen Schaltpositionen sieht die DE 19936946 C1 eine mit einer Schwenkwelle verbundene Scheibe mit umfangseitigen Rastausnehmungen vor, in die ein federnd gelagerter Raststift eingreift. Zur automatischen Rückstellung des Handhebels in eine Ruhestellung greift eine Zugfeder an diesen an. Die zusätzlich zur Lagerung des Handhebels unabhängig von dieser ausgeführten Rückstellungs- und Rastfunktionen erfordern jeweils zusätzliche Bauteile und besitzen einen zusätzlichen Raumbedarf. Durch die an ihn angreifende Zugfeder wird die Schwenkbewegung des Handhebels nur in einer Bewegungsrichtung gegen die Federkraft gebremst. Andere Mittel zum stabilisierenden Abbremsen der Schwenkbewegungen des Handhebels werden von der DE 19936946 C1 nicht offenbart.From the DE 19936946 C1 is a command ship for marine propulsion with a guided in a shift gate, known in two levels pivoting hand lever known. For locking the shift lever in its switching positions sees the DE 19936946 C1 a disc connected to a pivot shaft with circumferential recesses in front of which engages a spring-mounted locking pin. For automatic return of the hand lever in a rest position engages a tension spring to this. In addition to the storage of the hand lever regardless of this carried out reset and locking functions each require additional components and have an additional space requirement. By acting on him tension spring pivotal movement of the hand lever is braked only in a direction of movement against the spring force. Other means for stabilizing braking the pivoting movements of the hand lever are of the DE 19936946 C1 not revealed.

Aus der DE 199 63 476 A1 ist ein Kommandogeber der vorgenannten Art bekannt, der zusätzlich um seine Längsachse in beide Drehrichtungen gegen eine Federwirkung verdrehbar gelagert ist und der ein die Drehbewegung erfassenden Sensor zur Ansteuerung eines Aggregats, bspw. einer Motorsteuerung, aufweist. Die zusätzlich zur Lagerung des Handhebels unabhängig von dieser ausgeführten Federdämpfung der Drehbewegung erfordert zusätzliche Bauteile und besitzt einen zusätzlichen Raumbedarf.From the DE 199 63 476 A1 a commander of the aforementioned type is known, which is rotatably mounted in addition to its longitudinal axis in both directions of rotation against a spring action and which detects a rotational movement detecting sensor for controlling an aggregate, for example. A motor control having. The addition to the storage of the hand lever regardless of this executed spring damping of the rotary motion requires additional components and has an additional space requirement.

Aus der DE 1 992 922 U ist eine Rastvorrichtung für einen Maschinentelegraphen bekannt, bei dem ein Kommandohebel mit einer Rastrolle verschiebbar auf einer Rastbahn geführt ist. Eine solche Vorrichtung besitzt je nach gewählter Höhe der Rastvorsprünge gegenüber den Rastausnehmungen entweder ein relativ hohes Losbrechmoment oder eine relativ labile Stellung in der jeweiligen Schaltposition. Ferner ist es vorteilhaft, den Kommandogeber auf einer Kreisbahn schwenkbar auszugestalten, anstatt linear verschiebbar, da dies bei der Bereitstellung eines gleichlangen Schaltwegs raumsparender ist und eine ergonomischere Bedienung ermöglicht.From the DE 1 992 922 U a locking device for a machine telegraph is known in which a command lever with a detent roller is displaceably guided on a detent track. Such a device has depending on the selected height of the locking projections relative to the recesses either a relatively high breakaway torque or a relatively unstable position in the respective switching position. Further, it is advantageous to pivot the command generator on a circular path, rather than linearly displaceable, since this is space-saving in the provision of the same length switching path and allows a more ergonomic operation.

Aus der DE 103 52 445 B4 ist ein Bremselement für das kontrollierte Öffnen und Schließen von Hauben, Fächern, Schubladen usw. bekannt. Das Bremselement umfasst einen Außenrotor mit einer eine Lagerschale bildenden Öffnung und ein in der Öffnung angeordneten Innenrotor, welche relativ zueinander drehbeweglich angeordnet sind, wobei der Innenrotor ein oder mehrere radial gegen eine Federkraft aufstellbare, einseitig mit diesem verbundene Bremsorgane aufweist, die jeweils in eine in die Mantelfläche des Innenrotors eingebrachte Ausnehmung eindrückbar sind und an der Innenfläche der Lagerschale anliegen. Das von der DE 103 52 445 B4 offenbarte Bremselement (so genanntes Minibremselement) ist aufgrund seiner räumlichen Dimensionierung nicht zum Einsatz als Kommandogeber geeignet und sieht auch kein manuell bedienbares Stellglied, etwa einen Stellhebel, oder Mittel zur Montage eines solchen Stellgliedes vor. Zudem übt das Bremselement aufgrund der identischen Ausrichtung des oder der Bremsorgane innerhalb der Rotationsebene nur in einer Bewegungsrichtung - gegen das Aufstellmoment der Bremsorgane - eine Bremsfunktion aus bzw. ist die Bremsfunktion in Gegenrichtung jedenfalls erheblich vermindert. Schließlich sieht das von der DE 103 52 445 B4 vorgeschlagene Bremselement keine Mittel zum Rasten des Innenrotors gegen den Außenrotor vor.From the DE 103 52 445 B4 is a braking element for the controlled opening and closing of hoods, compartments, drawers, etc. known. The brake element comprises an outer rotor with a bearing shell forming an opening and an inner rotor disposed in the opening, which are rotatably mounted relative to each other, wherein the inner rotor one or more radially against a spring force can be erected, one-sided connected to this braking members, each in a in the lateral surface of the inner rotor introduced recess can be pressed and bear against the inner surface of the bearing shell. That of the DE 103 52 445 B4 disclosed brake element (so-called Minibremselement) is not suitable for use as a command station due to its spatial dimensions and also provides no manually operated actuator, such as a lever, or means for mounting such an actuator before. In addition, the brake element exerts due to the identical orientation of the or the brake elements within the plane of rotation only in one direction - against the Aufstellmoment the brake elements - a braking function or the braking function in the opposite direction is at least significantly reduced. Finally that looks from the DE 103 52 445 B4 proposed brake element no means for locking the inner rotor against the outer rotor before.

Brems-Rasteinheiten sind auch aus US4905537 , FR2359979 , US4646588 oder JP2009286165 bekannt.Brake detents are also off US4905537 . FR2359979 . US4646588 or JP2009286165 known.

OFFENBARUNG DER ERFINDUNGDISCLOSURE OF THE INVENTION

Der Erfindung liegt die Aufgabe zugrunde, eine Lagerungseinheit für einen manuell bedienbaren Kommandogeber mit einer integrierten kombinierten Brems-/Rastfunktion zu schaffen, die möglichst kompakt und einfach aufgebaut ist und einfach und kostengünstig hergestellt und montiert werden kann.The invention has for its object to provide a storage unit for a manually operated command transmitter with an integrated combined braking / locking function, which is as compact and simple as possible and can be easily and inexpensively manufactured and assembled.

Die Aufgabe wird erfindungsgemäß durch eine Brems-/Rasteinheit nach Anspruch 1 gelöst, vorteilhafte Ausführungen sind in den Unteransprüchen beschrieben.The object is achieved by a braking / locking unit according to claim 1, advantageous embodiments are described in the subclaims.

Den Kern der Erfindung bildet eine Brems-Rasteinheit für Kommandogeber mit einem Außenrotor mit einer einen Lagerring bildenden kreisrunden Öffnung und einem in der Öffnung angeordneten Innenrotor, welche relativ zueinander drehbeweglich angeordnet sind, wobei eines der beiden Rotorelemente in seiner Lage statisch fixiert und das andere Rotorelement entweder mit einem manuell bedienbaren Stellglied ausgebildet oder mit einem solchen verbindbar ausgestaltet ist und der Innenrotor mit mindestens drei radial in Umfangsrichtung angeordneten und einseitig mit diesem verbundenen Federarmen ausgebildet ist, welche jeweils in eine in der Mantelfläche des Innenrotors befindliche Ausnehmung eindrückbar sind, wobei mindestens ein Federarm an seinem freien Ende mit einem Rastmittel ausgebildet ist, welches lösbar form- und kraftschlüssig mit mindestens einer korrespondierenden Rastausnehmung in der Lauffläche des Lagerrings zusammenwirkt und mindestens zwei Federarme jeweils paarweise innerhalb der Rotationsebene zueinander gegenläufig angeordnet und an ihren freien Enden jeweils mit einem Bremsmittel ausgebildet sind und wobei die Federarme über die Brems- und Rastmittel jeweils radial kraftschlüssig auf die Lauffläche des Lagerrings wirken. Das jeweils in seiner Lage statisch fixierte Rotorenelement dient als in seiner Lage fixierter Stator (Innen- oder Außenstator), indem es beispielsweise an oder auf einer Konsole oder einem aufgeständerten Gehäuse montiert ist. Das jeweils andere, in diesem drehbeweglich gelagerte Rotorenelement (Innen- oder Außenrotor) dient der Veränderung der Schaltposition, indem es entweder mit einem manuell bedienbaren Stellglied, beispielsweise einem Stellhebel, ausgebildet ist oder mit einem solchen verbindbar ausgestaltet ist, indem es beispielsweise Bohrungen zum Anschrauben eines Stellhebels aufweist. Die in Umfangsrichtung angeordneten Federarme mit Bremsmitteln üben je nach Drehrichtung unterschiedliche Reibmomente auf die Lauffläche aus. Dieses ist in der Drehrichtung gegen das Aufstellmoment des jeweiligen Federarms größer als in der gegenläufigen Richtung. Indem die Federarme mit Bremsmitteln in der Rotationsebene jeweils paarweise zueinander gegenläufig angeordnet sind, summieren sich die beiden durch sie ausgeübten Reibmomente jeweils zu einem identischen Gesamtreibmoment, wodurch die Brems-/Rasteinheit in beide Drehrichtungen im Wesentlichen gleichmäßig stabilisierend abgebremst wird. Die Rastausnehmung(en) in der Lauffläche des Lagerrings repräsentieren jeweils die Schaltposition(en) der Brems-/Rasteinheit. Indem der oder die Federarm(e) mit Rastmittel in der Schaltposition jeweils formschlüssig in die korrespondierende Rastausnehmung in der Lauffläche des Lagerrings eingreift, ist die Brems-/Rasteinheit in der jeweiligen Stellung stabilisiert. Bei einer erneuten Verstellung wird oder werden der oder die jeweiligen Federarm(e) mit Rastmittel in die jeweilige Ausnehmung in der Mantelfläche des Innenrotors eingedrückt, wobei das Rastmittel die jeweilige Rastausnehmung wieder verlässt.The core of the invention is a brake-locking unit for command transmitter with an outer rotor with a bearing ring forming a circular opening and an opening disposed in the inner rotor, which are arranged rotatably relative to each other, one of the two rotor elements statically fixed in position and the other rotor element is formed either with a manually operable actuator or designed with such a connectable and the inner rotor is arranged with at least three radially arranged in the circumferential direction and one side connected to this spring arms, which are each pressed into a recess located in the lateral surface of the inner rotor, wherein at least one Spring arm is formed at its free end with a locking means which releasably positively and non-positively cooperates with at least one corresponding recess in the running surface of the bearing ring and at least two spring arms in pairs inn half of the plane of rotation are arranged in opposite directions and are each formed at their free ends with a braking means and wherein the spring arms via the brake and locking means in each case act radially frictionally on the running surface of the bearing ring. The respectively in its position statically fixed rotor element serves as fixed in its position stator (inside or outside stator), for example, by being mounted on or on a console or an elevated housing. The other, in this rotatably mounted rotor element (inner or outer rotor) is used to change the switching position by either with a manually operated actuator, For example, a lever, is formed or configured with such a connectable by having, for example, holes for screwing a control lever. The spring arms arranged in the circumferential direction with braking means exert different friction moments on the running surface depending on the direction of rotation. This is greater in the direction of rotation against the pitching moment of the respective spring arm than in the opposite direction. By the spring arms with braking means in the plane of rotation are arranged in pairs opposite each other in opposite directions, the two friction moments exerted by them add up to an identical Gesamtreibmoment, whereby the brake / locking unit is braked substantially uniformly stabilizing in both directions. The latching recess (s) in the running surface of the bearing ring each represent the switching position (s) of the brake / latch unit. By the or the spring arm (s) engages with locking means in the switching position in each case form-fitting manner in the corresponding recess in the running surface of the bearing ring, the brake / locking unit is stabilized in the respective position. In a renewed adjustment or the respective spring arm (s) is pressed with latching means in the respective recess in the lateral surface of the inner rotor, wherein the latching means leaves the respective latching recess again.

Eine noch größere Gleichmäßigkeit der in beide Drehrichtungen ausgeübten Bremswirkungen wird erreicht, indem bei einer Brems-Rasteinheit mit insgesamt mindestens vier Federarmen mindestens zwei Federarme mit Rastmitteln vorgesehen und jeweils paarweise innerhalb der Rotationsebene zueinander gegenläufig angeordnet sind, wobei die Rastmittel in einem gemeinsamen radialen Abschnitt angeordnet sind und jeweils synchron mit der oder den Rastausnehmung(en) zusammenwirken. Auch die Federarme mit Rastmitteln wirken radial kraftschlüssig auf die Lauffläche des Lagerrings und üben somit ein gewisses Reibmoment gegen die Verdrehung der Brems-/Rasteinheit aus. Dieses ist in der Drehrichtung gegen das Aufstellmoment des jeweiligen Federarms größer als in der gegenläufigen Richtung. Indem die Federarme mit Rastmitteln innerhalb der Rotationsebene jeweils paarweise zueinander gegenläufig angeordnet sind, ist auch das über die Rastmittel ausgeübte Gesamtreibmoment in beiden Drehrichtungen gleich.An even greater uniformity of the braking effects exerted in both directions of rotation is achieved by providing at least two spring arms with latching means in a brake-latching unit with a total of at least four spring arms and arranged in pairs opposite each other within the plane of rotation, the latching means being arranged in a common radial section are and in each case in synchronism with the or the recess (s) cooperate. The spring arms with locking means act radially non-positively on the running surface of the bearing ring and thus exert a certain frictional torque against the rotation of the brake / latch unit. This is greater in the direction of rotation against the pitching moment of the respective spring arm than in the opposite direction. By the spring arms are arranged with locking means within the plane of rotation in pairs opposite to each other in opposite directions, and the force exerted on the locking means Gesamtreibmoment is the same in both directions of rotation.

Indem in der vorstehenden Ausführung die Rastmittel jeweils eines Federarmpaares in einem gemeinsamen radialen Abschnitt angeordnet sind und jeweils synchron mit derselben Rastausnehmung zusammenwirken, ist beim Lösen der Rastung in beide Drehrichtungen zugleich ein identisches Losbrechmoment gewährleistet, ohne dass für jedes Federarmpaar eine zusätzliche zweite Rastausnehmung für das zweite Rastmittel in der Lauffläche des Lagerrings vorgesehen sein muss. Hierzu sind die Rastmittel eines Federarmpaares innerhalb desselben radialen Abschnitts vorzugsweise in Umfangsrichtung nebeneinander angeordnet. Dies gewährleistet eine kompakte Bauweise unter Beibehaltung eines in beide Richtungen gleichmäßigen Losbrechmoments.By in the above embodiment, the locking means are each a Federarmpaares arranged in a common radial portion and respectively synchronously cooperate with the same recess, at the same time an identical breakaway torque is ensured when releasing the detent in both directions without an additional second recess for each spring arm second locking means must be provided in the running surface of the bearing ring. For this purpose, the locking means of a Federarmpaares within the same radial portion are preferably arranged adjacent to each other in the circumferential direction. This ensures a compact design while maintaining a steady in both directions breakaway torque.

Für eine exaktere Einstellbarkeit der Brems-/Rastkräfte und eine Vergrößerung des Einsatzbereichs der Brems-/Rasteinheit sind die Federarme mit Bremsmitteln und/oder die Federarme mit Rastmitteln druckfederbelastet ausgestaltet, wobei die Druckfedern im Innenrotor angeordnet sind und radial auf die Federarme wirken. In dieser Ausführung wird der für das gewünschte Reibmoment der Bremsmittel und den hinreichend stabilen Sitz der Rastmittel erforderliche Radialkraft im Wesentlichen durch die Vorspannung der Druckfedern erzeugt. Druckfedern können bauartbedingt bei einer entsprechend vorgegebenen Vorspannung und Federkraft mit einer sehr viel kleineren Federrate ausgeführt werden als dies bei lediglich als Blattfedern ausgebildeten Federarmen möglich ist. Somit kann die Federkraft und damit in der Folge auch die von Ihnen auf die Brems-und Rastmittel ausgeübte Radialkraft auch bei unterschiedlichen Bauteiltoleranzen stets nahezu konstant ausgestaltet werden. Ferner können die für das gewünschte Reibmoment und die gewünschte Stabilität des Sitzes der Rastmittel in den Rastausnehmungen erforderlichen Radialkräfte - unabhängig voneinander - variiert und an unterschiedliche Anforderungen angepasst werden.For a more precise adjustability of the brake / latching forces and an increase in the range of application of the brake / latch unit, the spring arms with brake means and / or the spring arms with latching means are configured spring-loaded, wherein the compression springs are arranged in the inner rotor and act radially on the spring arms. In this embodiment, the required for the desired friction torque of the braking means and the sufficiently stable seat of the locking means radial force is generated substantially by the bias of the compression springs. Compression springs can be designed due to the design at a correspondingly predetermined preload and spring force with a much smaller spring rate than is possible with only designed as leaf springs spring arms. Thus, the spring force and thus also the radial force exerted by you on the brake and locking means can always be made almost constant even with different component tolerances. Furthermore, the radial forces required for the desired friction torque and the desired stability of the seat of the latching means in the latching recesses - independently of each other - can be varied and adapted to different requirements.

Für eine besonders einfach und kostengünstige Herstellung und Montage der Brems-Rasteinheit sind die Federarme, Rastmittel und Bremsmittel mit dem Innenrotor als einteiliges Bauteil ausgeführt. Die Brems-/Rasteinheit besteht in dieser Ausgestaltung mit sämtlichen erforderlichen Funktionselementen lediglich aus zwei Bauteilen.For a particularly simple and cost-effective production and assembly of the brake-locking unit, the spring arms, locking means and braking means are designed with the inner rotor as a one-piece component. The braking / locking unit consists in this embodiment with all the necessary functional elements only two components.

Indem in der vorstehenden Ausführung der Innen- und Außenrotor als Kunststoff-Spritzteile ausgeführt sind, kann die Herstellung weiter vereinfacht und Kosten weiter reduziert werden. Ferner gewährleistet diese Ausführung ein sehr geringes Gesamtgewicht der Vorrichtung.By in the above embodiment, the inner and outer rotor as plastic injection molded parts are executed, the production can be further simplified and costs can be further reduced. Furthermore, this design ensures a very low overall weight of the device.

Eine Verbesserung der Leichtgängigkeit der Brems-/Rasteinheit wird erreicht, indem die Rotorelemente mit einer gemeinsamen Kugellagerung ausgeführt sind.An improvement in the smooth running of the brake / latch unit is achieved by the rotor elements are designed with a common ball bearing.

Zur Verbesserung der Bedienung sind die Rotorelemente mit einer Anschlagsbegrenzung ausgebildet, welche den ihren drehbeweglichen Freiheitsgrad begrenzt. Auf diese Weise wird die Erstreckung des Schaltwegs der Brems-/Rasteinheit auf die Schaltpositionen begrenzt.To improve the operation of the rotor elements are formed with a stop limit, which limits their rotatable degree of freedom. In this way, the extension of the switching path of the brake / latch unit is limited to the switching positions.

Zur automatischen Erfassung der Stellposition der Brems-Rasteinheit ist das drehbewegliche Rotorelement mit einem Sensormagneten ausgebildet. Dies ermöglicht bespielweise im Zusammenwirken mit einem korrespondierenden Hall-Sensor eine berührungslose Erfassung der Winkelstellung des drehbeweglichen Rotorelements und somit auch eines mit diesem verbundenen Stellglieds.For automatic detection of the parking position of the brake-locking unit, the rotatable rotor element is formed with a sensor magnet. This allows recordable, in cooperation with a corresponding Hall sensor, a non-contact detection of the angular position of the rotatable rotor element and thus also an associated with this actuator.

Weitere die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung bevorzugter Ausführungsbeispiele der Erfindung anhand der Figuren näher dargestellt. Es zeigen:

Figur 1
eine perspektivische Explosivdarstellung einer Brems-/Rasteinheit für einen Kommandogeber,
Figur 2
eine perspektivische Frontaldarstellung der Brems-/Rasteinheit gemäß Figur 1 im Montagezustand,
Figur 3
eine perspektivische Aufsichtsdarstellung einer alternativen Ausführung des Innenrotors einer Brems-/Rasteinheit gemäß der Figuren 1 und 2,
Figur 4
eine perspektivische Schnittdarstellung einer weiteren Ausführung der Brems-/Rasteinheit,
Figur 5
eine perspektivische Frontaldarstellung der zusammengesetzten Brems-/Rasteinheit gemäß Figur 4.
Further measures improving the invention will be described in more detail below together with the description of preferred embodiments of the invention with reference to FIGS. Show it:
FIG. 1
an exploded perspective view of a brake / latch unit for a command generator,
FIG. 2
a perspective front view of the brake / latch unit according to FIG. 1 in the assembled state,
FIG. 3
a perspective top view of an alternative embodiment of the inner rotor of a brake / latch unit according to the FIGS. 1 and 2 .
FIG. 4
a perspective sectional view of another embodiment of the Brake / catch unit,
FIG. 5
a perspective front view of the composite brake / latch unit according to FIG. 4 ,

Die Brems-/Rasteinheit gemäß der Figuren 1 und 2 besteht aus einem Außenrotor 1 und einem Innenrotor 2, welcher mit drei radial in Umfangsrichtung angeordneten und mit diesem einseitig fest verbundenen, als Blattfedern ausgestalteten Federarmen 3, 3' und 3" ausgebildet ist. Unterhalb der Federarme 3,3' und 3" befinden sich in der Mantelfläche des Innenrotors 2 jeweils korrespondierende Ausnehmungen, in welche die Federarme 3, 3' und 3" eindrückbar sind. Die Federarme 3 und 3' sind an ihrem freien Ende mit den Bremsmitteln mit 4 und 4', der Federarm 3" mit dem Rastmittel 5 ausgebildet. Die Federarme 3, 3', 3", die Bremsmittel 4, 4' und das Rastmittel 5 sind mit dem Innenrotor 2 als einteiliges Bauteil ausgeführt. Der Außenrotor 1 weist eine kreisrunde Öffnung auf, welche einen Lagerring mit der Lauffläche 6 zur Aufnahme des Innenrotors 2 bildet. Der Außenrotor 1 ist mit drei Rastausnehmungen 7, 7' und 7" ausgebildet, welche der formschlüssigen Aufnahme des Rastmittels 5 dienen und die entsprechende Schaltpositionen der Brems-/Rasteinheit bestimmen. Zur Montage werden die Federarme 3, 3', 3" in die jeweils korrespondierenden Ausnehmungen in der Mantelfläche des Innenrotors 2 gedrückt und der Innenrotor 2 in den Außenrotor 1 eingesetzt. Aufgrund der hierdurch erzeugten Vorspannung wirken die Federarme 3, 3', 3" im montierten Zustand gemäß Figur 2 radial kraftschlüssig auf die Lauffläche 6 des Außerrotors 1. Hierdurch wird insbesondere über die Bremsmittel 4 und 4' ein Reibmoment erzeugt, das einer Drehbewegung des Innenrotors 2 gegen den Außenrotor 1 entgegenwirkt. Die Vorspannung der Federarme 3, 3' ist hierbei derart gewählt, dass diese die für das gewünschte Reibmoment erforderliche Radialkraft erzeugen. Die beiden in Umfangsrichtung angeordneten Federarme 3 und 3' üben über die Bremsmittel 4 und 4' je nach Drehrichtung unterschiedlichen Reibmomente auf die Lauffläche 6 aus. Dieses ist in der Drehrichtung gegen das Aufstellmoment des jeweiligen Federarms größer als in der gegenläufigen Richtung. Indem die beiden Federarme 3 und 3'in der Rotationsebene zueinander gegenläufig angeordnet sind, summieren sich die beiden durch sie ausgeübten Reibmomente jeweils zu einem identischen Gesamtreibmoment, wodurch die Brems-/Rasteinheit in beide Drehrichtungen im Wesentlichen gleichmäßig stabilisierend abgebremst wird. Die Vorspannung des Federarms 3" ist derart gewählt, dass ein hinreichend stabiler form- und kraftschlüssigen Sitz des Rastmittels 5 in den Rastausnehmungen 7, 7' und 7" in den Schaltpositionen bei einem gleichzeitig möglichst niedrigen Losbrechmoment beim Lösen des Sitzes gewährleistet ist. Die Vorspannung wird also so gewählt, das eine ungewollte Verstellung durch Vibrationen im Fahrbetrieb oder eine leichte Berührung hinreichend sicher vermieden wird, gleichzeitig jedoch eine feinfühlige Verstellung ohne allzu hohen Kraftaufwand ermöglicht ist. Durch das zusätzliche Führungsmittel 8 ist ein rotationssymmetrischer Sitz des Innenrotors 2 im Außenrotor gewährleistet. Bei der Brems-/Rasteinheit gemäß der Figuren 1 und 2 dient der Außenrotor 1 als Stator, indem er über die radial angeordnete Gewindebohrung 9 mit einem Gehäuse verbindbar ist und so im Einbauzustand in seiner Lage statisch fixiert ist. Der Innenrotor 2 ist im Einbauzustand drehbeweglich im Außenrotor 2 angeordnet und dient der manuell Veränderung der Schaltposition mittels eines Stellhebels, der über die stirnseitigen Bohrungen 10 und 10' an den Innenrotor 2 anschraubbar ist.The brake / lock unit according to FIGS. 1 and 2 consists of an outer rotor 1 and an inner rotor 2, which is formed with three spring arms 3, 3 'and 3 "arranged radially in the circumferential direction and fixedly connected to the latter on one side, designed as leaf springs, below the spring arms 3, 3' and 3" in the lateral surface of the inner rotor 2 respectively corresponding recesses into which the spring arms 3, 3 'and 3 "can be pressed in. The spring arms 3 and 3' are at their free end with the braking means 4 and 4 ', the spring arm 3" with the Detent 5 is formed. The spring arms 3, 3 ', 3 ", the brake means 4, 4' and the latching means 5 are designed as a one-piece component with the inner rotor 2. The outer rotor 1 has a circular opening which has a bearing ring with the running surface 6 for receiving the inner rotor The outer rotor 1 is formed with three latching recesses 7, 7 'and 7 ", which serve for the positive reception of the latching means 5 and determine the corresponding switching positions of the brake / latching unit. For assembly, the spring arms 3, 3 ', 3 "are pressed into the respective corresponding recesses in the lateral surface of the inner rotor 2 and the inner rotor 2 is inserted into the outer rotor 1. Due to the prestressing produced thereby, the spring arms 3, 3', 3" act in the assembled state according to FIG. 2 In this way, a frictional torque is generated in particular via the braking means 4 and 4 ', which counteracts a rotational movement of the inner rotor 2 against the outer rotor 1. The bias of the spring arms 3, 3 'is in this case selected such that they generate the radial force required for the desired friction torque. The two spring arms 3 and 3 'arranged in the circumferential direction exert different friction moments on the running surface 6 via the brake means 4 and 4' depending on the direction of rotation. This is greater in the direction of rotation against the pitching moment of the respective spring arm than in the opposite direction. By the two spring arms 3 and 3 'in the plane of rotation are arranged in opposite directions to each other, the two friction moments exerted by them add up in each case to an identical Gesamtreibmoment, whereby the brake / latch unit is braked substantially uniformly stabilizing in both directions of rotation. The bias of the spring arm 3 "is chosen such that a sufficiently stable positive and non-positive fit of the locking means 5 is ensured in the recesses 7, 7 'and 7" in the switching positions at the same time the lowest possible breakaway torque when loosening the seat. The preload is thus chosen so that an unwanted adjustment by vibration while driving or a light touch is sufficiently reliably avoided, but at the same time a sensitive adjustment is made possible without too much effort. By the additional guide means 8, a rotationally symmetrical seat of the inner rotor 2 is ensured in the outer rotor. In the brake / latch unit according to the FIGS. 1 and 2 the outer rotor 1 serves as a stator by being connected via the radially arranged threaded bore 9 with a housing and is fixed statically in the installed state in its position. The inner rotor 2 is rotatably mounted in the installed state in the outer rotor 2 and is used to manually change the switching position by means of a control lever which can be screwed on the front side bores 10 and 10 'to the inner rotor 2.

Figur 3 zeigt eine alternative, mit dem Außenrotor 1 kompatible Ausführungsform eines Innenrotors 2' mit zwei innerhalb der Rotationsebene zueinander gegenläufig angeordneten Federarmen 3a und 3b mit Rastmitteln 5a und 5b. Bei Tests mit der Ausführungsform des Innenrotors 2 gemäß der Figuren 1 und 2 zeigte sich, dass auch der Federarm 3" über das Rastmittel 5 bei der für ein hinreichend stabiler form- und kraftschlüssigen Sitz in den Rastausnehmungen 7, 7' und 7" erforderlichen Vorspannung ein gewisses Reibmoment auf die Lauffläche 6 des Außenrotors 1 ausübt. Dieses Reibmoment ist in der Drehrichtung gegen das Aufstellmoment des Federarms 3" größer als in der gegenläufigen Richtung. Indem dieses durch die beiden innerhalb der Rotationsebene zueinander gegenläufig angeordneten Federarme 3a und 3b mit Rastmitteln 5a und 5b ersetzt wird, ist auch das über die beiden Rastmittel 5a und 5b ausgeübte Gesamtreibmoment in beiden Drehrichtungen gleich und eine absolute Gleichmäßigkeit der in beide Drehrichtungen ausgeübten Bremswirkung gewährleistet. Da die beiden Rastmittel 5a und 5b zudem in einem gemeinsamen radialen Abschnitt angeordnet sind und jeweils synchron mit den Rastausnehmungen 7, 7' und 7" zusammenwirken, ist in dieser Ausführung des Innenrotors 2' zudem ein in beide Drehrichtungen identisches Losbrechmoment gewährleistet, ohne dass zusätzliche Rastausnehmungen in der Lauffläche 6 geschaffen werden müssen. FIG. 3 shows an alternative, compatible with the outer rotor 1 embodiment of an inner rotor 2 'with two within the rotation plane to each other in opposite directions arranged spring arms 3a and 3b with locking means 5a and 5b. In tests with the embodiment of the inner rotor 2 according to the FIGS. 1 and 2 It was found that the spring arm 3 "exerts a certain frictional torque on the running surface 6 of the outer rotor 1 via the latching means 5 in the prestressing required for a sufficiently stable positive and non-positive fit in the latching recesses 7, 7 'and 7". This friction torque is greater in the direction of rotation than the setting moment of the spring arm 3 "in the opposite direction 5a and 5b ensure equal friction in both directions of rotation and ensure absolute uniformity of the braking action exerted in both directions of rotation Since the two locking means 5a and 5b are also arranged in a common radial section and cooperate synchronously with the locking recesses 7, 7 'and 7'' , is in this embodiment of the inner rotor 2 'also identical in both directions of rotation Losbrechmoment ensured without additional recesses in the tread 6 must be created.

Die Figuren 4 und 5 zeigen eine alternative Ausführung der Brems-/Rasteinheit. Der Außenrotor 1' und der Innenrotor 2" sind mit einer integrierten Kugellagerung ausgeführt und bilden mit den Rillenelementen 11a und 11b eine gemeinsame umlaufende Laufrille für in ihr angeordneten Kugeln, von denen auf der Schnittdarstellung gemäß Figur 4 die angeschnittenen Kugeln 12 und 12' erkennbar sind. Da das Lager als vollkugeliges Lager ausgeführt ist, ist kein separater Kugelkäfig erforderlich. Die Laufrille ist ausreichend tief, so dass auch axiale Kräfte aufgenommen werden können. Hierdurch ist sichergestellt, dass ein mit den stirnseitigen Bohrungen 10"' und 10"" des Innenrotors 2" verbundener, in den Figuren 4 und 5 nicht dargestellter Stellhebel in axialer und radialer Richtung spielfrei geführt ist und kein nennenswertes zusätzliche Reibungsmoment durch Lagerreibung erzeugt wird. Sämtliche Federarme mit Brems- und Rastmitteln, von denen auf der Schnittdarstellung gemäß Figur 4 lediglich der Federarm 3'" erkennbar ist, sind in dieser Ausgestaltung druckfederbelastet ausgeführt. Hierzu sind im Innenrotor 2" unter den Federarmen jeweils Druckfedern angeordnet. In der Schnittdarstellung gemäß Figur 4 sind hierbei lediglich die unter den Rastmitteln 5a' und 5b' angeordnete Druckfeder 13 und teilweise die unter dem Bremsmittel 4" angeordnete Druckfeder 13' dargestellt. Zur Begrenzung des Freiheitsgrads des Innenrotors 2 und damit auch zur Begrenzung des Schwenkweges eines mit den stirnseitigen Bohrungen 10'" und 10"" des Innenrotors 2" verbundenen, in den Figuren 4 und 5 nicht dargestellten Stellhebels sind der Innenrotor 2" und der Außenrotor 1' stirnseitig mit einer Anschlagsbegrenzung ausgeführt. Ein mit dem Innenrotor 2" stirnseitig verbundenes Anschlagselement 14a ist zwischen zwei stirnseitig mit dem Außenrotor 1' verbundenen Anschlagelementen 14b und 14b' geführt wodurch der Freiheitsgrad der Drehbewegung des Innenrotors 2" auf insgesamt 140° begrenzt wird. Der Innenrotor 2" ist stirnseitig zudem mit einer Ausnehmung 15 zur Aufnahme eines in den Figuren 4 und 5 nicht dargestellten Sensormagneten versehen. Im Zusammenwirken mit einem korrespondierenden, in den Figuren 4 und 5 ebenfalls nicht dargestellten Hall-Sensor, der senkrecht zur Rotationsachse der Brems-/Rasteinheit in einem Abstand von 0,5 bis 2mm vor dem Sensormagneten angeordnet ist, gestattet dies eine berührungslose Erfassung der Winkelstellung des Innenrotors 2" und somit auch eines mit diesem verbundenen Stellhebels. Zur Abdichtung des Geräte-Innenraums der Brems- Rasteinheit gegenüber der Umgebung verfügt der Außenrotor 1' über eine umlaufende Dichtnut 16 zur Aufnahme eines (nicht dargestellten) O-Ringes. Die Abdichtung gegenüber dem Stellhebel erfolgt über eine Lippendichtung. Die Lauffläche der Dichtlippe 17 wird durch einen Schutzring 18 gegen direkte Beaufschlagung durch Spritz- oder Strahlwasser geschützt.The FIGS. 4 and 5 show an alternative embodiment of the brake / latch unit. The outer rotor 1 'and the inner rotor 2 "are designed with an integrated ball bearing and form with the groove elements 11a and 11b a common circumferential groove for balls arranged in it, of which on the sectional view FIG. 4 the truncated balls 12 and 12 'can be seen. Since the bearing is designed as a fully spherical bearing, no separate ball cage is required. The groove is sufficiently deep, so that axial forces can be absorbed. This ensures that one connected to the frontal bores 10 "'and 10""of the inner rotor 2", in the FIGS. 4 and 5 unillustrated lever in the axial and radial direction is performed without play and no significant additional friction torque is generated by bearing friction. All spring arms with braking and locking means, of which on the sectional view according to FIG. 4 Only the spring arm 3 '"is recognizable, in this embodiment designed to be spring-loaded.For this purpose, compression springs are respectively arranged in the inner rotor 2" under the spring arms. In the sectional view according to FIG. 4 in this case, only the compression spring 13 arranged under the latching means 5a 'and 5b' and partially the compression spring 13 'arranged under the braking means 4' are shown, in order to limit the degree of freedom of the inner rotor 2 and thus also to limit the pivoting path of one with the frontal bores 10 '. "and 10""of the inner rotor 2", in the FIGS. 4 and 5 A stop element 14a which is connected to the inner rotor 2 "at the end is guided between two stop elements 14b and 14b 'which are connected to the outer rotor 1' by means of the inner rotor 2" whereby the degree of freedom of the rotational movement is guided of the inner rotor 2 "is limited to a total of 140 °. The inner rotor 2" is also provided with a recess 15 for receiving one in the front side FIGS. 4 and 5 provided sensor magnet, not shown. In cooperation with a corresponding, in the FIGS. 4 and 5 Hall sensor, also not shown, which is arranged perpendicular to the axis of rotation of the brake / locking unit at a distance of 0.5 to 2mm in front of the sensor magnet, this allows a non-contact detection of the angular position of the inner rotor 2 "and thus one with this connected control lever. For sealing the device interior of the brake locking unit relative to the environment of the outer rotor 1 'has a circumferential sealing groove 16 for receiving a (not shown) O-ring. The seal against the adjusting lever via a lip seal. The running surface of the sealing lip 17 is protected by a protective ring 18 against direct exposure to spray or jet water.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1, 1'1, 1 '
Außenrotorouter rotor
2, 2', 2"2, 2 ', 2 "
Innenrotorinner rotor
3, 3', 3", 3"', 3a, 3b3, 3 ', 3 ", 3"', 3a, 3b
Federarmespring arms
4, 4', 4"4, 4 ', 4 "
Bremsmittelbraking means
5, 5a, 5b, 5a', 5b'5, 5a, 5b, 5a ', 5b'
Rastmittellatching means
66
Laufflächetread
7, 7', 7"7, 7 ', 7 "
Rastausnehmungrecess
88th
Führungsmittelguide means
99
Gewindebohrungthreaded hole
10, 10', 10", 10'"10, 10 ', 10 ", 10'"
Bohrungdrilling
11a, 11b11a, 11b
Rillenelementgrooved member
12, 12'12, 12 '
KugelBullet
13, 13'13, 13 '
Druckfedercompression spring
14a, 14b'14a, 14b '
Anschlagselementestop elements
1515
Ausnehmungrecess
1616
Dichtnutsealing groove
1717
Dichtlippesealing lip
1818
Schutzringprotective ring

Claims (9)

  1. Braking and locking unit for a control-signal generator, comprising an outer rotor (1, 1'), having a circular opening that forms a bearing ring, and an inner rotor (2, 2', 2") arranged in the opening, said rotors being arranged so as to be rotatable relative to one another, one of the two rotor elements being fixed in the position thereof in a stationary manner, and the other rotor element either comprising a manually operable actuator or designed to be connectable to an actuator of this type, and the inner rotor (2, 2', 2") comprising at least three spring arms (3, 3', 3", 3"', 3a, 3b) which are arranged radially in the peripheral direction, are connected to said inner rotor at one end, and can each be pushed into a recess located in the lateral face of the inner rotor (2, 2', 2"), characterised in that at least one spring arm (3", 3a, 3b) comprises an locking means (5, 5a, 5b, 5a', 5b') at the free end thereof, which means releasably interacts, in a positive and non-positive manner, with at least one corresponding locking recess in the raceway (6) of the bearing ring, and at least two spring arms (3, 3', 3") are arranged in the rotation plane and so as to run counter to one another in pairs in each case, and each have a braking means (4, 4', 4") at the free end thereof, the spring arms (3, 3', 3", 3"', 3a, 3b) each acting on the raceway (6) of the bearing ring in the radial direction and in a non-positive manner by means of the braking means (4, 4', 4") and the locking means (5, 5a, 5b, 5a', 5b).
  2. Braking and locking unit according to claim 1, comprising at least four spring arms (3, 3', 3", 3"', 3a, 3b), characterised in that at least two spring arms (3a, 3b) are provided with locking means (5a, 5b) and are arranged in the rotation plane and so as to run counter to one another in pairs in each case.
  3. Braking and locking unit according to claim 2, characterised in that the locking means (5a, 5b, 5a', 5b') of each spring arm pair are arranged in a common radial portion and in each case interact with the locking recess(es) (7, 7', 7") in a synchronous manner.
  4. Braking and locking unit according to any of claims 1 to 3, characterised in that the spring arms (3"') having braking means (4") and/or the spring arms having locking means (5a', 5b') are compression-spring-loaded, the compression springs (13, 13') being arranged in the inner rotor (2") and acting radially on the spring arms (3"').
  5. Braking and locking unit according to any of claims 1 to 4, characterised in that the spring arms (3, 3', 3", 3"', 3a, 3b), the locking means (5, 5a, 5b, 5a', 5b') and the braking means (4, 4', 4") are formed as an integral component with the inner rotor.
  6. Braking and locking unit according to claim 5, characterised in that the inner rotor (2, 2', 2") and the outer rotor (1, 1') are formed as plastics moulded parts.
  7. Braking and locking unit according to any of claims 1 to 6, characterised in that the rotor elements have a common ball bearing.
  8. Braking and locking unit according to any of claims 1 to 7, characterised in that the rotor elements have a stop limit.
  9. Braking and locking unit according to any of claims 1 to 8, characterised in that the rotatable rotor element comprises a sensor magnet.
EP16707615.7A 2015-01-15 2016-01-15 Braking and locking unit for a control-signal generator Active EP3245127B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015000192.2A DE102015000192B4 (en) 2015-01-15 2015-01-15 Brake locking unit for command transmitter
PCT/DE2016/000015 WO2016112893A1 (en) 2015-01-15 2016-01-15 Braking-stopping unit for command issuer

Publications (2)

Publication Number Publication Date
EP3245127A1 EP3245127A1 (en) 2017-11-22
EP3245127B1 true EP3245127B1 (en) 2018-08-01

Family

ID=55452971

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16707615.7A Active EP3245127B1 (en) 2015-01-15 2016-01-15 Braking and locking unit for a control-signal generator

Country Status (7)

Country Link
US (1) US10401897B2 (en)
EP (1) EP3245127B1 (en)
CN (1) CN107406132B (en)
DE (1) DE102015000192B4 (en)
DK (1) DK3245127T3 (en)
ES (1) ES2692023T3 (en)
WO (1) WO2016112893A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012017123B4 (en) 2011-08-31 2023-03-16 Marquardt Gmbh Signal transmitters, in particular electric rotary switches

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021072653A1 (en) * 2019-10-15 2021-04-22 深圳市大疆创新科技有限公司 Internal rotor assembly testing system and movable platform
US11243556B2 (en) * 2020-03-10 2022-02-08 Whirlpool Corporation Knob assembly for a cooking appliance and method of assembling

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE244533C (en)
DE1992922U (en) 1968-01-09 1968-08-29 Siemens Ag DEVICE FOR REPLACING INDICATIVE LIGHTS WITH CRUSH FOOT BASES, HOLDING INTO SOCKETS BY INTENSIFYING SPRINGS.
IT938712B (en) * 1971-10-12 1973-02-10 Gai G CONTROL DEVICE TO OPERATE WITH A SINGLE LEVER THE ENGAGEMENT OF FORWARD GEAR OR REVERSE GEAR AND THE ACCELERATOR OF AN ENGINE PREFERABLY TO BACKHOE COMBUSTION
JPS59146322A (en) 1983-02-12 1984-08-22 Shimano & Co Ltd Variable speed operating device for bicycle
US4646588A (en) * 1985-10-21 1987-03-03 Merriman/Yacht Specialties, Inc. Pedestal base single lever control unit
DD244533A1 (en) 1985-12-20 1987-04-08 Schiffbau Veb K CHASSIS REMOTE CONTROL FOR DRIVING MACHINES ON SHIPS
DE3828545A1 (en) 1988-08-23 1990-03-01 Bayer Ag AMINOMETHYLHETEROCYCLES, METHOD FOR THE PRODUCTION THEREOF, THEIR USE IN PEST CONTROL, AND NEW INTERMEDIATE PRODUCTS
US5222901A (en) 1991-03-18 1993-06-29 Marine Brokers, Inc. Redundant marine engine control system
DE19936946C1 (en) 1999-08-05 2001-01-25 Peter Mueller Hand lever control for motor and sports boats
DE19963476A1 (en) 1999-12-28 2001-07-19 Peter Mueller Hand lever control for motor and sports boats
DE20305291U1 (en) * 2003-04-01 2003-06-18 Schneider Eng Gmbh Swivel bearing for a flap, in particular for the flap in front of a tank cap in a motor vehicle
DE102006052589B3 (en) 2006-11-08 2008-04-17 Preh Gmbh Rest producing device for operating unit of motor vehicle, has spring unit with two spring arms that are formed in parallel, so that spring arms lie at identical recess or rising of rest contour, where unit is formed from bent flat spring
US7475841B2 (en) * 2007-01-09 2009-01-13 Hannay Reels, Inc. Spring retractable reel having a pneumatic retraction governor
JP2009286165A (en) * 2008-05-27 2009-12-10 Toyoda Gosei Co Ltd Turning device
DE102011100986B3 (en) 2011-05-10 2012-10-18 Behr-Hella Thermocontrol Gmbh Operating device, in particular for a vehicle component

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012017123B4 (en) 2011-08-31 2023-03-16 Marquardt Gmbh Signal transmitters, in particular electric rotary switches

Also Published As

Publication number Publication date
CN107406132A (en) 2017-11-28
WO2016112893A1 (en) 2016-07-21
DK3245127T3 (en) 2018-11-05
US20180329446A1 (en) 2018-11-15
ES2692023T3 (en) 2018-11-29
US10401897B2 (en) 2019-09-03
EP3245127A1 (en) 2017-11-22
DE102015000192A1 (en) 2016-07-21
DE102015000192B4 (en) 2023-07-20
CN107406132B (en) 2019-05-17

Similar Documents

Publication Publication Date Title
EP0175996B1 (en) Drive unit particularly for moving window screens, gliding roofs, seats and similar vehicle devices
EP1659298B1 (en) Linear drive
WO2016074660A1 (en) Rotary heat exchanger device
WO2006087365A2 (en) Electromotive linear drive
EP3245127B1 (en) Braking and locking unit for a control-signal generator
DE102010052920A1 (en) Fahrwerkaktuator
EP3417183B1 (en) Ball joint
DE102005007205B3 (en) Electromotor linear drive e.g. for adjustment functions, has rotary spindle nut with linear speed components of displacing tube controlled by braking arrangement
EP1032522B1 (en) Electromotive actuator for a motor vehicle steering system
EP3155276B1 (en) Disengaging overload clutch with latching by way of magnetically loaded control elements
WO2009153166A1 (en) Clamping device for positional fixing of an adjustable vehicle steering column
DE10352445A1 (en) Automotive fuel tank inlet cover flap swivels on pivot bolt with brake
DE102018123052B4 (en) Electric clutch actuator with rotation angle sensor
DE102015224612A1 (en) Actuator, clutch and motor vehicle
DE102015201104B3 (en) Oldham
DE102006042478A1 (en) Electromotive actuator for the deflection of a mechanical part
EP3575637B1 (en) Motor vehicle drive assembly
DE102018123053B4 (en) Electric clutch actuator with four-point bearing for spindle nut
DE102011018730A1 (en) Drehflügeltürbetätiger
DE102019133406A1 (en) Push rod guide assembly, steering actuator and method for manufacturing a push rod guide assembly
DE102017116271A1 (en) Spindle drive with overload clutch
DE102015201596B4 (en) Locking mechanism for a spindle drive
DE3106094C1 (en) Lockable ball coupling that can be engaged and disengaged, especially for hand crank gear
DE3802017C2 (en) Automatic adjustment device for a disc brake
DE102017102809B4 (en) Device for stepless locking of a vehicle door

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: 20170802

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

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

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
INTG Intention to grant announced

Effective date: 20180130

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

Ref country code: AT

Ref legal event code: REF

Ref document number: 1023965

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180815

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: 502016001594

Country of ref document: DE

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Effective date: 20181022

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2692023

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20181129

REG Reference to a national code

Ref country code: NO

Ref legal event code: T2

Effective date: 20180801

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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: 20180801

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: 20180801

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: 20181201

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: 20181102

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: 20180801

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: 20181101

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: 20180801

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: 20180801

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

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: 20180801

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: 20180801

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: 20180801

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

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: 20180801

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: 20180801

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: 20180801

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502016001594

Country of ref document: DE

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: 20180801

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: 20180801

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: 20190503

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

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: 20180801

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: 20180801

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: CH

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

Effective date: 20190131

Ref country code: LI

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

Effective date: 20190131

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: 20190115

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: 20180801

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: 20180801

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: 20181201

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: 20180801

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: 20160115

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1023965

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210115

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: 20210115

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

Ref country code: MK

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: 20180801

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

Ref country code: ES

Payment date: 20230201

Year of fee payment: 8

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

Ref country code: IT

Payment date: 20230103

Year of fee payment: 8

Ref country code: DE

Payment date: 20221220

Year of fee payment: 8

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230529

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

Ref country code: GB

Payment date: 20231219

Year of fee payment: 9

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

Ref country code: NO

Payment date: 20231221

Year of fee payment: 9

Ref country code: NL

Payment date: 20231219

Year of fee payment: 9

Ref country code: LU

Payment date: 20231219

Year of fee payment: 9

Ref country code: FR

Payment date: 20231219

Year of fee payment: 9

Ref country code: DK

Payment date: 20231219

Year of fee payment: 9

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

Ref country code: BE

Payment date: 20231219

Year of fee payment: 9

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

Ref country code: ES

Payment date: 20240202

Year of fee payment: 9

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

Ref country code: DE

Payment date: 20231219

Year of fee payment: 9