EP2534390A2 - Frein électrique - Google Patents

Frein électrique

Info

Publication number
EP2534390A2
EP2534390A2 EP11717166A EP11717166A EP2534390A2 EP 2534390 A2 EP2534390 A2 EP 2534390A2 EP 11717166 A EP11717166 A EP 11717166A EP 11717166 A EP11717166 A EP 11717166A EP 2534390 A2 EP2534390 A2 EP 2534390A2
Authority
EP
European Patent Office
Prior art keywords
brake
electric drive
spindle element
spindle
housing
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.)
Withdrawn
Application number
EP11717166A
Other languages
German (de)
English (en)
Inventor
Michael Reich
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.)
Hanning and Kahl GmbH and Co KG
Original Assignee
Hanning and Kahl GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hanning and Kahl GmbH and Co KG filed Critical Hanning and Kahl GmbH and Co KG
Publication of EP2534390A2 publication Critical patent/EP2534390A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2247—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers
    • F16H25/2252—Planetary rollers between nut and screw
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/90—Braking
    • F05B2260/902—Braking using frictional mechanical forces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/90—Braking
    • F05B2260/903—Braking using electrical or magnetic forces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/003—Position, angle or speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/24—Electric or magnetic using motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement
    • F16D2125/48—Rotating members in mutual engagement with parallel stationary axes, e.g. spur gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement
    • F16D2125/50—Rotating members in mutual engagement with parallel non-stationary axes, e.g. planetary gearing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the invention relates to a brake for example, wind turbines with at least one brake actuator, which is operatively connected to a planetary roller screw unit and an electric drive for adjusting the brake actuator between a braking position and an axially offset non-braking position thereof, wherein the planetary roller screw unit a plurality of in the circumferential direction distributed arranged threaded roller bodies, which are in threaded engagement on the one hand with a rotatably connected to the electric drive spindle element and the other with a stationary housing, and that the threaded roller bodies about their own axes, which are each arranged parallel to an axis of the spindle member, and are arranged rotatably about the axis of the spindle member.
  • a brake for wind turbines is known in which a force acting on a brake disc brake actuator (brake shoe) is coupled to an electric drive to reciprocate.
  • the electric drive comprises an electric motor which is coupled via a lever with a transmission which converts the pivoting movement into an axial movement.
  • the gear can be used as a spindle or ball screw or
  • CONFIRMATION COPY Planetary roller screw be formed.
  • the transmission comprises an axially displaceable and non-rotatably guided in a housing spindle element, at one end of the brake actuator is fixedly arranged.
  • a disadvantage of the known brake is that due to the pivoting lever coupling between the electric motor and the spindle element results in a power flow chain, which has a relatively low efficiency result.
  • the brake has a relatively large volume of construction.
  • EP 1 837 555 A1 discloses a brake with a direct-acting electric actuator which directly converts the rotational movement of an electric drive into an axial movement of a body which actuates a brake operating element (brake shoe) between a braking position and a non-braking position acting on a brake disk. and moved.
  • the acting on the brake actuator body is formed as a threaded roller body of a planetary roller screw unit, which is in threaded engagement with a trained as a spindle element rotor shaft of the electric motor and the other with a stationary ring housing.
  • the threaded roller bodies are arranged rotatably about their own axis and as a planetary roller body about an axis of the spindle element.
  • the axis of the threaded roller body is parallel to the axis of the spindle member.
  • the known brake allows space-saving direct action of force on the brake actuator.
  • a disadvantage of the known brake is that the power flow extends directly from the threaded roller bodies via two thrust bearings on the brake actuator; Consequently, the threaded roller bodies are arranged to exert force.
  • the bearings must be designed extremely precise in order to synchronously back and forth of the To ensure brake actuator.
  • a bellows is required for the central positioning of the brake actuator.
  • Object of the present invention is to develop a brake such that relatively low pressure forces are generated with little effort, with a relatively high efficiency and a low overall volume are guaranteed.
  • the invention in conjunction with the preamble of claim 1, characterized in that the brake actuating element is coupled only to the spindle element.
  • the particular advantage of the invention is that relatively high compressive forces are transmitted by means of a planetary roller screw unit by utilizing a relatively high efficiency to a brake actuator. It is a simple and robust introduction of force causes, the power flow of a rotatably coupled to the electric drive spindle element runs on the brake actuator. Thread rolling bodies of the planetary roller screw unit only act force-transmitting, but not force-exerting. By the planetary roller screw unit relatively high compressive and tensile forces can be generated. The electric drive has a relatively low reduction, which reduces space requirements and costs.
  • the brake actuating element is connected via a thrust bearing with the spindle element.
  • a thrust bearing with the spindle element.
  • the Effort for the introduction of force can be reduced.
  • only a single thrust bearing or a single bearing unit along the power transmission path is required, so that reduced manufacturing costs and maintenance costs can be kept low.
  • the spindle element is bell-shaped with a bottom and a hollow cylinder section projecting from the bottom, wherein at least part of the electric drive is arranged in the hollow cylinder section.
  • differently designed electric drives can thus be coupled to the spindle element or to the planetary roller threaded unit.
  • an electric motor or an electric motor-gear unit may be arranged depending on the application in the cavity of the spindle member, an electric motor or an electric motor-gear unit.
  • the electric drive can thus be designed variably to the requirements of the use of the brake without the basic structure of the brake would have to be changed.
  • the electric drive may be arranged outside the housing, wherein it may preferably be coupled via a gear transmission or a belt transmission with the spindle element.
  • the electric drive can thus be configured independently of the dimension of the spindle element.
  • the preferably more threaded roller body in a common arranged annular cage with recesses for the threaded engagement of the threaded roller body are advantageously mounted freely movable in the axial direction.
  • the cage enables improved guidance of the threaded roller bodies in a gap between an outer side of the spindle element and an inner side of the housing.
  • the electric drive and / or the spindle element is fixedly connected to a hood which extends axially outwardly with a longitudinal wall on the housing.
  • a centered mounting of the spindle element or of the brake actuating element can thereby be effected.
  • the hood and / or the housing may have detection means for determining the relative position of the hood to the housing in the axial direction and / or in the circumferential direction.
  • this can be done by a torque and / or position-dependent, for example, load-dependent shutdown of the electric motor.
  • the detection means can be used to detect a brake lining wear of the brake actuator and then either to generate a corresponding signal to replace the brake actuator or to increase the force acting on the brake actuator pressure force.
  • the detection means are arranged in a main force generating plane, so that the detection can be done without tilting.
  • limit switches and, with the same interacting noises, limit switches are used as detection means.
  • this can be done depending on the force of rotation due to a rotation of the spindle member about its axis and / or due to its axial movement a shutdown of the brake.
  • FIG. 1 shows a radial section through a brake according to a first embodiment of the invention in a non-braking position
  • FIG. 2 shows a radial section of the brake according to FIG. 1 in a braking position
  • FIG. 3 shows an axial section through the brake according to FIG.
  • FIG. 4 shows a radial section through a brake according to a second embodiment of the invention in a braking position
  • Figure 5 shows a radial section through a brake according to a third embodiment of the invention in a braking position
  • Figure 6 shows a radial section through a brake according to a fourth embodiment of the invention in a braking position.
  • a brake 1 according to the invention can preferably be used in wind turbines for decelerating wind turbine blades.
  • the brake 1 can also be used in brake systems for solar tracking arrangements or for brake systems in the field of mechanical engineering or in medical technology.
  • the brake 1 essentially comprises a brake actuation element 2 (brake shoe), a planetary roller screw unit 3 coupled to the brake actuation element 2 and an electric drive 4 coupled to the planetary roller screw unit 3.
  • the brake actuating element 2 on the one hand, has a holding disk 5, which is coupled to a bell-shaped spindle element 7 via a thrust bearing 6 designed as a needle bearing.
  • the brake actuating element 2 on a side facing away from the spindle element 7 of the retaining plate 5, a brake pad 8, which in the operation of the brake 1, ie in the axial movement of the brake actuator 2 from a non-braking position according to Figure 1 in a braking position according to Figure 2, in a printing system position is spent to a brake disc 9.
  • a further brake pad 8 ' is arranged, which is fixedly connected to a foot 10 of a stationary and the spindle element 7 comprehensive housing 11 is connected.
  • the housing 11 is formed as a ring housing, the outer and / or inner Mantelwandungen extend at least partially cylindrical.
  • the foot 10 and the ring housing 11 thus form a brake caliper.
  • the bell-shaped spindle element 7 has a radially extending bottom 12 and a side facing away from the brake actuator 2 side of the bottom 12 of the same projecting hollow cylinder portion 13. In this hollow cylinder section 13, the electric drive 4 is at least partially arranged.
  • the electric drive 4 may consist only of an electric motor whose drive shaft is fixedly connected to the spindle element 7 and / or the retaining plate 5.
  • the electric drive 4 may also consist of an electric motor and a gear transmission coupled thereto, wherein the gear transmission is arranged between the electric motor and the bottom 12 of the spindle element 7.
  • An output-side gear of the gear transmission is fixedly connected to the spindle member 7 and / or the retaining plate 5.
  • the gear transmission is designed as a planetary gear which is completely enclosed in the hollow cylinder section 13 of the spindle element 7.
  • the electric motor is preferably arranged partially within the hollow cylinder section 13.
  • the electric drive 4 is fixedly connected to a hood 15 which surrounds the ring housing 11 with a cylindrical longitudinal wall 16 in the amount of the planetary roller screw unit 3.
  • a hood 15 which surrounds the ring housing 11 with a cylindrical longitudinal wall 16 in the amount of the planetary roller screw unit 3.
  • the hood 15 is arranged guided relative to the annular housing 11 in the axial direction.
  • the hood 15 is thus arranged guided over the guide means 17 in the axial direction and in the circumferential direction.
  • a ring seal 18 At a free end of the longitudinal wall 16 is disposed between the same and the annular housing 11, a ring seal 18.
  • the planetary roller screw unit 3 has a plurality of threaded roller bodies 19 distributed in the circumferential direction, which essentially extend in an annular gap between an outer wall 20 of the hollow cylinder section 13 and an inner wall 21 of the annular housing 11.
  • the threaded roller body 19 are solid and cylindrical and each extending between radially extending boundary walls 22, 22 'of a one-piece annular cage 23.
  • the boundary walls 22, 22' of the cage 23 each have openings in which free ends of the threaded roller body 19 are mounted.
  • the threaded roller body 19 of which preferably each a threaded roller body 19 between the boundary walls 22, 22 'extend, have an external thread, so that they are in threaded engagement with the outer wall 20 of the hollow cylindrical portion 13 of the spindle member 7 and the other with the inner wall 21 of the ring housing 11.
  • the threaded roller body 19 are rotatably supported about its own axis and the other about an axis A of the spindle member 7. Since the spindle member 7 is fixed or rotationally fixed to a drive shaft of the electric drive 4, are actuated upon actuation of the electric Drive 4, the spindle element 7 and the threaded roller body 19 is set in rotation.
  • the housing 11 is formed in sections annularly at least in the region of the threaded roller body 19th
  • FIG. 2 illustrates a flow of force flow between the annular housing 11 and the brake disk 9 through the arrow K. It can be seen that the force flow acts on the brake actuating element 2 via the spindle element 7 and the axial bearing 6.
  • the outer wall 20 of the hollow cylinder portion 13, the inner wall 21 of the ring housing 11 and the threaded roller body 19 have such a thread pitch that the brake actuator 2 is moved between the non-braking position and the braking position and vice versa by a predetermined stroke H.
  • the electric drive 4 is arranged coaxially with the spindle element 7.
  • the electric drive 4 is located at least partially in the hollow cylinder section 13 of the spindle element 7, so that the assembly consisting of planetary roller screw unit 3 and electric drive 4 has a compact structure.
  • the hood 15 and / or the ring housing 11 has detection means.
  • the annular housing 11 has an end switch on a rim facing the hood 15. ter 24, which may be formed, for example, as a microswitch. Once the hood 15 reaches a contact lug 25 of the limit switch 24 with its radial surface, the limit switch 24 triggers a shutdown of the electric drive 4 or blocking thereof in the braking position.
  • the contact pin 27 cooperates with an inner side of the longitudinal wall 16 of the hood 15 arranged cam 28 so that the non-braking position, ie the extended position of the spindle member 7 to the ring housing 11, is recognized.
  • the limit switch 26 is triggered, the electric drive 4 is switched off.
  • limit switches 29 are also provided as detection means, which are circumferentially attached to the outside of the ring housing 11.
  • Contact pins 30 of the limit switches 29 cooperate with axially extending cam strips 31 or point-shaped cams which are arranged on an inner side of the longitudinal wall 16.
  • FIG. 3 also shows that the hood 15 is supported by spring elements 32 in the circumferential direction with respect to the ring housing 11. Since the limit switch 29 are arranged in an outer circumferential recess of the ring housing 11, they are accessible from the outside and easy to use adjustable.
  • the limit switches 29 trigger and can thus switch off the electric drive 4 as a function of the angle of rotation.
  • a rotational position and / or longitudinal position-dependent deactivation of the spindle element 7 is ensured by the aforementioned detection means. In particular, this can be done in a simple manner, a pre-adjustment or readjustment with wear of the brake pad 8, 8 '.
  • the electric drive 4 can also be arranged outside the housing (annular housing 11).
  • the electric drive 4 is connected via a screw 39 with a solid trained spindle element 1 '.
  • the electric drive 4 is mounted coaxially with the spindle element 7 '.
  • the hood 15 has a corresponding central bore.
  • the electric drive 4 is coupled via a gear transmission 40 with the spindle element 7 '.
  • the electric drive 4 is arranged offset parallel to the spindle element 7 ', wherein it is supported by a support member 42 on the longitudinal wall 16 of the hood 15.
  • the electric drive 4 has - as in the other embodiments - an electric motor and a transmission, wherein the transmission is coupled to a pinion 43 of the gear transmission 40.
  • the pinion 43 is in engagement with a coaxial with the lock element 7 'arranged th gear 44, which is preferably fixed by screwing with one of the retaining plate 5 facing away from the end face of the spindle element V.
  • the spindle element 7 is - as in the previous embodiment - fixedly coupled to an integrally connected to the retaining plate 5 pin 45.
  • the gear 44 has a hub by means of which it is firmly connected to the hood 15.
  • the gear 44 may be non-positively and / or positively connected to the hood 15.
  • the electric drive 4 instead of directly via the pinion 43 with a coaxial with the spindle member 7 'arranged wheel 46 via a gear transmission or a belt transmission 41 or a chain transmission with the same be coupled.
  • an open belt transmission 41 is provided, wherein a belt 47 on the one hand, the pinion 43 and on the other hand co-axial with the spindle member 7 'arranged pulley 46 wraps.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Braking Arrangements (AREA)

Abstract

L'invention concerne un frein comportant au moins un élément d'actionnement de frein en liaison fonctionnelle avec une unité filetée à rouleaux satellites et un entraînement électrique pour déplacer l'élément d'actionnement de frein entre une position de serrage de frein et une position de libération de frein axialement décalée, l'unité filetée à rouleaux satellites comportant une pluralité de corps rouleaux satellites répartis périphériquement, s'engrenant d'une part avec un élément broche solidaire en rotation avec l'entraînement électrique, et d'autre part avec un boîtier fixe. Les corps rouleaux satellites sont disposés rotatifs autour de leur propres axes respectivement parallèles à un axe de l'élément broche, et autour de l'axe de l'élément broche, l'élément d'actionnement de frein étant uniquement accouplé à l'élément broche.
EP11717166A 2010-02-10 2011-02-10 Frein électrique Withdrawn EP2534390A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010001782 2010-02-10
DE102010038418A DE102010038418B4 (de) 2010-02-10 2010-07-26 Elektrische Bremse
PCT/DE2011/000126 WO2011098074A2 (fr) 2010-02-10 2011-02-10 Frein électrique

Publications (1)

Publication Number Publication Date
EP2534390A2 true EP2534390A2 (fr) 2012-12-19

Family

ID=44316768

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11717166A Withdrawn EP2534390A2 (fr) 2010-02-10 2011-02-10 Frein électrique

Country Status (5)

Country Link
US (1) US20120292140A1 (fr)
EP (1) EP2534390A2 (fr)
CN (1) CN103109104B (fr)
DE (1) DE102010038418B4 (fr)
WO (1) WO2011098074A2 (fr)

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EP3246219A1 (fr) * 2016-05-19 2017-11-22 Haldex Brake Products Aktiebolag Unité de transmission de force de freinage, sous-ensemble de frein et groupe d'ensembles de frein
DE202017100294U1 (de) * 2017-01-20 2018-04-25 Peter Lutz Windkraftanlage
CN108061114B (zh) * 2018-01-03 2024-02-13 徐州五洋科技股份有限公司 一种用于风力发电机的刹车制动装置
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US11333229B2 (en) * 2020-03-17 2022-05-17 ZF Active Safety US Inc. Roller screw system
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Also Published As

Publication number Publication date
DE102010038418A1 (de) 2011-08-11
US20120292140A1 (en) 2012-11-22
CN103109104B (zh) 2016-05-04
WO2011098074A2 (fr) 2011-08-18
DE102010038418B4 (de) 2011-11-24
WO2011098074A3 (fr) 2013-09-12
CN103109104A (zh) 2013-05-15

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