WO2005015044A1 - Freins - Google Patents

Freins Download PDF

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Publication number
WO2005015044A1
WO2005015044A1 PCT/GB2004/003023 GB2004003023W WO2005015044A1 WO 2005015044 A1 WO2005015044 A1 WO 2005015044A1 GB 2004003023 W GB2004003023 W GB 2004003023W WO 2005015044 A1 WO2005015044 A1 WO 2005015044A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
shaft
force
ball ramp
ramp mechanism
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.)
Ceased
Application number
PCT/GB2004/003023
Other languages
English (en)
Inventor
Jonathan Paul Davies
Brian Farley
Neil Christian Tyler
Neil Andrew Venables
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.)
Smiths Group PLC
Original Assignee
Smiths Group PLC
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 Smiths Group PLC filed Critical Smiths Group PLC
Publication of WO2005015044A1 publication Critical patent/WO2005015044A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/36—Brakes with a plurality of rotating discs all lying side by side
    • 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
    • F16D2121/20—Electric or magnetic using electromagnets
    • F16D2121/22—Electric or magnetic using electromagnets for releasing a normally applied brake
    • 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
    • F16D2125/36—Helical cams, Ball-rotating ramps
    • F16D2125/38—Helical cams, Ball-rotating ramps with plural cam or ball-ramp mechanisms arranged concentrically with the brake rotor axis
    • 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
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/08—Self-amplifying or de-amplifying mechanisms
    • F16D2127/12—Self-amplifying or de-amplifying mechanisms having additional frictional elements

Definitions

  • This invention relates to brake assemblies of the kind including a casing and a first brake coupled between a shaft and the casing.
  • the invention is more particularly, but not exclusively, concerned with wing tip brakes.
  • An aircraft high lift system such as including a flap or slat is often displaced by mechanical actuators powered by rotation of a shaft extending along the length of the wing and driven by a motor towards the aircraft body.
  • the shaft system may be provided with a brake towards the wing tip.
  • the brake is applied to stop rotation of the shaft and hence movement of the control surfaces if an anomaly is detected in the drive system, to protect against asymmetry of the control surfaces in the drive systems on the two wings.
  • the brake may be hydraulically operated but this requires hydraulic piping and electrical control wiring to extend along the length of the wing, which adds to the weight and cost. Electrically- operated solenoid brakes may alternatively be used but those capable of stopping rotation of the shaft are large and heavy.
  • Electrically-operated brakes including a ball ramp mechanism have been proposed. These can be lighter and smaller than conventional electrical brakes but, as previously proposed, they need to be manually released after actuation. In an aircraft, this would mean that, once operated, the brakes would be locked on and the control surfaces could not be moved until the aircraft had landed.
  • a brake assembly of the above-specified kind characterised in that the assembly includes a ball ramp mechanism having a first part coupled with the first brake, a second brake coupled to a second part of the ball ramp mechanism, and an actuator operable to apply a force to the second brake such as to slow movement of the second part of the ball ramp mechanism and thereby cause the first part of the ball ramp mechanism to apply a force to the first brake so as to brake rotation of the shaft, and such that the braking force on the shaft releases when the actuator ceases applying the force to the second brake.
  • the actuator is preferably electrical and may include an armature and electrical windings.
  • the actuator preferably includes a resilient member operable to apply the force to the second brake.
  • the actuator is preferably arranged to apply force to the second brake in the absence of electrical power to the actuator.
  • the first brake may include a plurality of brake plates some of which are mounted with the casing and others of which are mounted with the shaft, the ball ramp mechanism being operable to apply a force urging the brake plates together and thereby apply a braking force to the shaft.
  • the second brake may include a plurality of brake plates some of which are mounted with the casing and others of which are mounted with the ball ramp mechanism.
  • the ball ramp mechanism preferably includes two parallel, spaced plates with a plurality of arc shaped grooves on opposed faces, the grooves being deepest towards a midpoint along their length and being shallower towards their ends, the mechanism including a ball retained between respective grooves in the two plates.
  • the shaft may be coupled to a control surface of an aircraft wing.
  • an aircraft control surface mechanism including first and second shafts extending along a part of the length of respective wings of an aircraft, a control surface coupled with each shaft, a drive for rotating the shafts about their length to effect movement of the respective control surface, an anomaly detector for sensing an anomaly in operation of the mechanism, and first and second brake assemblies connected with respective ones of the first and second shafts, each brake assembly including a casing and a first brake coupled between the respective shaft and the casing, characterised in that the brake mechanism includes a ball ramp mechanism having a first part coupled with the first brake, a second brake coupled to a second part of the ball ramp mechanism, and an actuator operable in response to an output from the anomaly detector to apply a force to the second brake such as to slow movement of the second part of the ball ramp mechanism and thereby cause the first part of the ball ramp mechanism to apply a force to the first brake so as to brake rotation of the shaft and thereby prevent further displacement of the control surface, and such that the braking force on the shaft releases when the brake mechanism includes a ball ramp mechanism having
  • Figure 1 is a simplified, plan view of an aircraft flap system including a brake assembly on each wing;
  • Figure 2 is a sectional side elevation view through one half of a brake assembly
  • Figure 3 illustrates a plate of the ball ramp mechanism.
  • the aircraft has two wings 1 and 2 extending laterally from opposite sides of its body 3.
  • Each wing supports two lift flaps 11 and 12, and 21 and 22 respectively on its trailing edge, which are extensible and deflectable to increase the lift provided by the wings such as during take-off and landing.
  • the flaps 11 and 12 on one wing 1 are coupled to a single shaft 13 extending along the major part of the length of the wing 1 parallel to and adjacent its trailing edge.
  • the coupling between the shaft 13 and the flaps 11 and 12 includes gearing (not shown), which steps down multiple rotations of the shaft into an angular displacement of the flaps.
  • the right wing 2 has a shaft 23 extending along its length coupled to the flaps 21 and 22.
  • the shafts 13 and 23 are rotated by a common drive unit 14 mounted at the inboard end of the shafts adjacent the body 3.
  • the drive unit 14 is controlled by a control unit 30.
  • each shaft 13 and 23 Mounted at the outer end of each shaft 13 and 23, towards the tip of each wing 1 and 2, there is a brake assembly 15, 25, which is also controlled by signals from the control unit 30. h particular, the control unit 30 supplies signals to actuate the brakes 15 and 25 when it detects an anomaly in displacement of the flaps 11, 12, 21 and 22 or their associated mechanism inconsistent with the displacement commanded, or when there is asymmetry between operation of the flaps on the two wings. This locks the shafts 13 and 23 to prevent further displacement of the flaps 11, 12, 21 and 22.
  • Sensors 31 located adjacent the shafts 13 and 23 or the flaps 11, 12, 21 and 22 supply signals to the control unit 30 for use in identifying an anomaly.
  • the brake assembly 25 includes an inner, axial shaft 100 of tubular form and cut with splines 101 on its outer surface at one end. These splines 101 are shaped to mate with similar splines (not shown) in a recess at the wing tip end of the shaft 23 so that the two shafts 100 and 23 rotate together.
  • the shaft 100 is supported at its right-hand end 102 by a bearing 103 mounted on a flange 104 fixed with the outer casing 105 of the assembly.
  • the casing 105 is generally cylindrical in shape and is formed of several parts held together by nuts and bolts.
  • the outer casing 105 is fixed to the structure of the wing 2 so that it cannot move relative to the wing.
  • a second bearing 106 supports the shaft 100 towards its opposite end, just to the right of the splines 101.
  • the second bearing 106 is fixed with a left-hand end flange 107 of the casing 105.
  • the left-hand end of the casing 105 contains a main brake unit 112.
  • This comprises a number of brake plate rotors 113 mounted by splines 114 on the shaft 100 so that they rotate with the shaft but can be displaced by a small distance axially along the shaft.
  • a respective stator plate 115 which are mounted on longitudinally- extending rods 116 fixed with the casing 105.
  • the mounting prevents the stator plates 113 rotating but they can slide along the rods by a small distance.
  • the brake plates 113 and 115 are contained at one end by a flange 117 fixed with the shaft 100 to the left of the plates.
  • the plates 113 and 115 are contacted by a second flange 118, which is slidable along the splines 114.
  • a disc spring mechanism 119 towards the right-hand end of the brake plates 113 and 115 holds them apart, so that no braking force is applied, until an external force is applied to push them together.
  • the right-hand end flange 118 is engaged by a ball ramp mechanism 120.
  • This comprises a first plate 121 in contact with the flange 118 and slidable along the splines 114.
  • the right-hand surface of the plate 121 has three grooves 122 of arc shape equally spaced around the plate and with their centre of curvature at the centre of the plate.
  • Each groove 122 is symmetrical about a radial line bisecting the groove and is deepest midway along its length, becoming shallower towards each end.
  • the mechanism 120 includes a second plate 123 having three grooves 124 on its left-hand surface, that is, the face opposed to the grooved face of the first plate 121, the grooves being of the same form as those on the first plate 121.
  • the second plate 123 is provided at the left-hand end of a tubular sleeve 125, which is supported at its right-hand end by a bearing 126 so that it is free to rotate about the axis of the shaft 100 but cannot move axially relative to the shaft.
  • the ball ramp mechanism 120 also includes three spherical metal bearing balls 127 between the two plates 121 and 123 and located in the grooves 122 and 124.
  • the inclination of the two grooves 122 and 124 at their ends are such that when the two plates 121 and 123 are rotated relative to one another the trapped balls 127 ride up the slope of the grooves in the two plates causing the plates to separate.
  • the left-hand plate 121 is constrained to rotate with the shaft 100 whereas the right- hand plate 123 is unconstrained and can rotate relative to the shaft but normally will be rotated with the left-hand plate.
  • a secondary brake unit 130 is located to the right of the ball ramp mechanism 120. This is similar to the main brake unit 112 but is only capable of applying a much smaller braking force.
  • the secondary brake unit 130 includes several brake rotor plates 131 mounted on longitudinally-extending splines 132 around the external surface of the sleeve 125 so that the plates rotate with the sleeve and can be moved a small distance along the length of the sleeve.
  • the stator brake plates 133 are mounted on the rods 116 fixed with the casing 105 so that they cannot rotate but can be displaced a small distance axially.
  • the right-hand end of the stack of brake plates 131 and 133 is engaged by the left-hand end of a cylindrical, soft- iron armature assembly 140, which is slidable axially of the brake assembly 25.
  • the armature assembly 140 is urged to the left by a helical spring 141 extending between an end flange 142 of the outer casing 105 and between a flange 143 towards the left-hand end of the armature.
  • the force applied by the spring 141 therefore, tends to apply a braking force between the two sets of brake plates 131 and 133 in the secondary brake unit 130.
  • the armature assembly 140 interacts electromagnetically with two electrical winding coils 150 fixed to the inside of the casing 105 so that the combination of the armature and coils provides actuation means in the form of an electrical solenoid.
  • the coils 150 and armature 140 form an actuator and are arranged so that when power is applied to the coils it causes an axial force on the armature acting against that of the spring 141, that is, tending to move the armature to the right. It can be seen, therefore, that when power is applied to the windings 150 the secondary brake 130 is off and when no power is applied, the secondary brake is on.
  • Alternative forms of actuator could be used.
  • control unit 30 applies power to the windings 150 in each brake assembly 15 and 25 so that the secondary brake 130 is held off. This allows the two plates 121 and 123 to rotate together and assume a configuration with minimum separation between them. This in turn ensures that no force is applied against the action of the spring 119 in the main brake unit 112 so that plates 113 and 115 of this brake unit are free to rotate relative to one another and no braking force is applied to the shaft 100.
  • the shafts 13 and 23 are, therefore, free to rotate to displace the flaps 11, 12, 21 and 22 as commanded.
  • the control unit 30 When an anomaly is detected, such as asymmetry between the displacement of the flaps or shafts in opposite wings, the control unit 30 immediately terminates supply of power to each brake assembly 15 and 25.
  • the spring 141 is now free to displace the armature 140 to the left, which applies a force pushing the stator and rotor brake plates 133 and 131 together. This increases friction between the plates 133 and 131 and applies a braking force between the casing 105 and the sleeve 125.
  • the sleeve 125 and the plate 123 therefore, stop rotating.
  • the other plate 121 of the ball mechanism 120 continues to rotate through a small angle causing the balls 127 to ride up the incline of the grooves 122 and 124 and force the two plates apart.
  • the control unit 30 supplies power to each brake assembly 15 and 25 to energize the coils 150 and pull the armature 140 against the action of the spring 141 to release the secondary brake unit 130.
  • the right-hand plate 123 of the ball ramp 120 can now rotate to allow the balls 127 to ride down the ramp of the grooves 122 and 124, aided by the spring 119, and thereby allow the left-hand plate 121 to move towards the other plate and release the braking force applied by the main brake unit 112 so that the shaft 100 can rotate freely.
  • the braking force that stops rotation of the shaft 100 is applied solely by the main braking unit 112 and the casing 105.
  • the axial load generated by the ball ramp mechanism 120 is contained within the braking unit 112 and the shaft 102 and does not influence the braking unit 130. This ensures that there is no risk of self-generated forces jamming the ball ramp mechanism 120. This arrangement enables the brake assembly to be released electrically, remotely without the need for manual unlocking.
  • the assembly of the present invention can be relatively compact and of low weight whilst still providing sufficient force rapidly to brake movement of the control surfaces.
  • the assembly is not confined to use in aircraft but could be used for braking other rotating mechanisms.
  • the brake assembly could readily be arranged to be normally off and be turned on when power is supplied to it.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

L'invention concerne un ensemble (25) de frein d'extrémité d'aile d'aéronef permettant une rotation de freinage d'un arbre (23, 100) comprenant un logement (105) comportant un premier frein (112) principal à deux ensembles de plaquettes de frein (113, 115) montées respectivement à l'arbre et au logement. Une force peut être appliquée pour activer le frein (112) principal au moyen d'un mécanisme (120) de rampe à balles, une première plaquette (121) étant reliée au frein principal et une seconde plaquette (123) étant reliée à un ensemble de plaquettes de frein (131) dans un frein secondaire (130). Le frein secondaire (130) comprend un second ensemble de plaquettes de frein (133) monté à l'intérieur du logement (105). Un ressort (141) placé dans un actionneur électrique applique une force dans le frein secondaire (130), ce qui permet de pousser les deux ensembles de plaquettes de frein (131) ensemble, tout en empêchant la rotation de la seconde plaquette (123) sur le mécanisme (120) de rampe à balles, au moyen du frein secondaire. Cela, entraîne le mouvement de la première plaque (121) vers le frein principal (112), tout en provoquant une force de freinage entre l'arbre (100) et le logement (105). Afin de libérer l'ensemble frein (25), une puissance est appliquée aux bobines (150) de l'actionneur, lequel applique une force au ressort (140) pour libérer à la fois, le frein secondaire (130) et le frein principal (112).
PCT/GB2004/003023 2003-07-31 2004-07-12 Freins Ceased WO2005015044A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0317908.2 2003-07-31
GB0317908A GB0317908D0 (en) 2003-07-31 2003-07-31 Brakes

Publications (1)

Publication Number Publication Date
WO2005015044A1 true WO2005015044A1 (fr) 2005-02-17

Family

ID=27799528

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2004/003023 Ceased WO2005015044A1 (fr) 2003-07-31 2004-07-12 Freins

Country Status (2)

Country Link
GB (1) GB0317908D0 (fr)
WO (1) WO2005015044A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009037106B4 (de) * 2008-08-14 2020-10-29 Hamilton Sundstrand Corp. Asymmetrie-Bremse mit großer Verstärkung
DE102020110427A1 (de) 2020-04-16 2021-10-21 Liebherr-Aerospace Lindenberg Gmbh Bremsvorrichtung für Steuersysteme von Flugzeugen

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1039165A2 (fr) * 1999-03-23 2000-09-27 Eaton Corporation Frein d'inertie de transmission avec anneau de blocage d'huile
GB2352784A (en) * 1999-08-04 2001-02-07 Moog Inc Energy-absorbing brake
EP1081405A2 (fr) * 1999-09-04 2001-03-07 Lucas Industries Limited Frein

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1039165A2 (fr) * 1999-03-23 2000-09-27 Eaton Corporation Frein d'inertie de transmission avec anneau de blocage d'huile
GB2352784A (en) * 1999-08-04 2001-02-07 Moog Inc Energy-absorbing brake
EP1081405A2 (fr) * 1999-09-04 2001-03-07 Lucas Industries Limited Frein

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009037106B4 (de) * 2008-08-14 2020-10-29 Hamilton Sundstrand Corp. Asymmetrie-Bremse mit großer Verstärkung
DE102020110427A1 (de) 2020-04-16 2021-10-21 Liebherr-Aerospace Lindenberg Gmbh Bremsvorrichtung für Steuersysteme von Flugzeugen

Also Published As

Publication number Publication date
GB0317908D0 (en) 2003-09-03

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