EP3245127B1 - Brems-rasteinheit für kommandogeber - Google Patents

Brems-rasteinheit für kommandogeber Download PDF

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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)
English (en)
French (fr)
Other versions
EP3245127A1 (de
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/de
Application granted granted Critical
Publication of EP3245127B1 publication Critical patent/EP3245127B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Braking Arrangements (AREA)
EP16707615.7A 2015-01-15 2016-01-15 Brems-rasteinheit für kommandogeber Active EP3245127B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015000192.2A DE102015000192B4 (de) 2015-01-15 2015-01-15 Brems-Rasteinheit für Kommandogeber
PCT/DE2016/000015 WO2016112893A1 (de) 2015-01-15 2016-01-15 Brems-rasteinheit für kommandogeber

Publications (2)

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

Family

ID=55452971

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16707615.7A Active EP3245127B1 (de) 2015-01-15 2016-01-15 Brems-rasteinheit für kommandogeber

Country Status (7)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012017123B4 (de) 2011-08-31 2023-03-16 Marquardt Gmbh Signalgeber, insbesondere elektrischer Drehschalter

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114270163A (zh) * 2019-10-15 2022-04-01 深圳市大疆创新科技有限公司 内转子组件测试系统以及可移动平台
US11243556B2 (en) * 2020-03-10 2022-02-08 Whirlpool Corporation Knob assembly for a cooking appliance and method of assembling

Family Cites Families (15)

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Publication number Priority date Publication date Assignee Title
DE244533C (es)
DE1992922U (de) 1968-01-09 1968-08-29 Siemens Ag Vorrichtung zum auswechseln von durch rastfedern in steckfassungen gehaltenen meldelampen mit quetschfusssockel.
IT938712B (it) * 1971-10-12 1973-02-10 Gai G Dispositivo di comando per azionare con un unica leva l innesto della marcia avanti o della marcia indie tro e l acceleratore di un motore preferibilmente a combustione in terna
JPS59146322A (ja) 1983-02-12 1984-08-22 Shimano & Co Ltd 自転車用変速操作装置
US4646588A (en) * 1985-10-21 1987-03-03 Merriman/Yacht Specialties, Inc. Pedestal base single lever control unit
DD244533A1 (de) 1985-12-20 1987-04-08 Schiffbau Veb K Fahrhebelfernbedienung fuer antriebsmaschinen auf schiffen
DE3828545A1 (de) 1988-08-23 1990-03-01 Bayer Ag Aminomethylheterocyclen, verfahren zu ihrer herstellung, ihre verwendung in schaedlingsbekaempfungsmitteln und neue zwischenprodukte
US5222901A (en) 1991-03-18 1993-06-29 Marine Brokers, Inc. Redundant marine engine control system
DE19936946C1 (de) 1999-08-05 2001-01-25 Peter Mueller Handhebelsteuerung für Motor- und Sportboote
DE19963476A1 (de) 1999-12-28 2001-07-19 Peter Mueller Handhebelsteuerung für Motor- und Sportboote
DE20305291U1 (de) 2003-04-01 2003-06-18 Dr. Schneider Engineering GmbH, 96317 Kronach Schwenklager für eine Klappe, insbesondere für die Klappe vor einem Tankverschluss in einem Kraftfahrzeug
DE102006052589B3 (de) 2006-11-08 2008-04-17 Preh Gmbh Vorrichtung zur Erzeugung einer Rast in einem Bedienelement
US7475841B2 (en) * 2007-01-09 2009-01-13 Hannay Reels, Inc. Spring retractable reel having a pneumatic retraction governor
JP2009286165A (ja) * 2008-05-27 2009-12-10 Toyoda Gosei Co Ltd 回動装置
DE102011100986B3 (de) 2011-05-10 2012-10-18 Behr-Hella Thermocontrol Gmbh Bedienvorrichtung, insbesondere für eine Fahrzeugkomponente

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012017123B4 (de) 2011-08-31 2023-03-16 Marquardt Gmbh Signalgeber, insbesondere elektrischer Drehschalter

Also Published As

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

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