WO2000031430A1 - Frein a disques a haute resistance thermique - Google Patents
Frein a disques a haute resistance thermique Download PDFInfo
- Publication number
- WO2000031430A1 WO2000031430A1 PCT/FR1999/002875 FR9902875W WO0031430A1 WO 2000031430 A1 WO2000031430 A1 WO 2000031430A1 FR 9902875 W FR9902875 W FR 9902875W WO 0031430 A1 WO0031430 A1 WO 0031430A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- housing
- thrust
- disc
- end wall
- bearing
- Prior art date
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
- 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
- F16D55/28—Brakes with only one rotating disc
-
- 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
- F16D2055/0004—Parts or details of disc brakes
- F16D2055/0058—Fully lined, i.e. braking surface extending over the entire disc circumference
-
- 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
- F16D2125/58—Mechanical mechanisms transmitting linear movement
- F16D2125/64—Levers
Definitions
- the invention relates to a disc friction device for a drive shaft.
- the field of application of the invention is slowing down or braking on transmission, in particular for heavy-duty road vehicles, for motor bogies of railway vehicles, or for industrial rotating machines.
- Disc brakes are also known using discs made of thermostructural composite material, in particular carbon / carbon composite material (C / C) which offer very good friction behavior and a significant gain in mass compared with metal disc brakes. traditional.
- C / C carbon / carbon composite material
- disc friction devices made of C / C material has already been envisaged for retarders or brakes on the transmission of heavy goods vehicles.
- the object of the invention is to provide a disc friction device for braking or slowing down an engine or transmission shaft, which has a very small footprint while allowing the use of discs made of thermostructural composite material and d '' pneumatic control.
- non-rotating housing having at least one end wall provided with a bearing for the rotary shaft
- the housing has a cage shape in which are housed the thrust structure, the disc assembly and the support structure, and comprises a first end wall on the side of the thrust structure, a second wall of end of the side of the support structure and a peripheral wall provided with ventilation openings,
- the actuating means consist of a pneumatic actuator mechanically connected to a central part of the thrust structure, through a central opening in the first end wall of the housing, and
- Thermal insulation means are arranged between the disc assembly and the outside of the housing on the side of the end wall provided with the bearing for the rotary shaft, comprising at least one thermal barrier located at the level of the bearing.
- the pneumatic actuator is fixed to the first end wall of the housing, on the side of the thrust structure, making the device compact.
- the pneumatic actuator is fixed to the second end wall of the housing and is connected to the thrust structure by at least one lever, so that an amplification of the pressure delivered by the actuator is obtained.
- H may be imparted to the central part of the thrust structure in the form of a recess housed in an axial passage surrounded by the discs, so that the mechanical connection between the actuator and the thrust structure extends at least in part in this axial passage, thus contributing to the compactness of the device.
- the pushing structure can be formed by a pushing piece having a central part connected to the actuator and an annular peripheral part, and by a set of cups fixed on this annular peripheral part and pressing against the external face of the first disc. stator, thus limiting the contact surfaces, and therefore the heat transfer between the discs and the thrust structure.
- the support structure can be formed by an annular support piece and a set of cups fixed on the support piece and pressing against the external face of the second stator disc.
- the rotational connection between the rotary shaft and the or each rotor disc can be achieved by means of a part fixed on the shaft and provided with jumpers which penetrate into notches formed at the inner periphery of the or each rotor disc, the jumpers being made of a material which does not conduct much heat in order to limit the transfer of heat between the discs and the rotary shaft.
- At least one heat shield located inside the housing between the disk assembly and the bearing for the rotary shaft.
- the heat shield can be carried by the support structure.
- the thermal barrier located at the level is for example constituted by at least one baffle imposing a tortuous path to the air along the level.
- This thermal barrier advantageously combined with a thermal screen inside the housing, makes it possible to effectively oppose the transfer of the heat generated by the friction of the discs to the driving or transmission members coupled to the rotary shaft. outside of the housing.
- FIG. 1 is a sectional view along the planes II of Figure 2 of an embodiment of a disc friction device according to the invention, for bogie brake motor of rail vehicle;
- - Figure 2 is a sectional view along the plane II-II of Figure 1;
- - Figure 3 is a sectional view along the planes m-i ⁇ of Figure 5 of another embodiment of a disc friction device according to the invention, for bogie brake motor of rail vehicle;
- Figure 4 is a sectional view along the IN-IN planes of Figure 4;
- FIG. 5 is a sectional view showing yet another embodiment of a disc friction device according to the invention for a heavy-duty road vehicle transmission brake
- FIG. 6 is a perspective view of the device of Figure 5.
- FIG. 7 is a detail view on a larger scale of the device in FIG. 5.
- FIGS. 1 and 2 illustrate a first embodiment of a friction device according to the invention in an application for a motor vehicle bogie brake.
- the friction device is mounted at the end of a drive axle shaft
- H comprises a set of coaxial discs comprising three stator discs 21, 23, 25 alternating with two rotor discs 22, 24, located between a thrust structure 30 and a support structure 40, inside a housing 50.
- the discs have the same axis A as the shaft 10.
- the braking of the shaft 10 is carried out by mutual tightening of the discs 21 to 25 between the thrust structure 30 and the support structure 40 under the effect of a pressure generated by a pneumatic actuator 60.
- the housing 50 has a first end wall 51 located on the side of the thrust structure, a second end wall 52 opposite the first and supporting the support structure, and a peripheral wall. This is materialized by bars 53 oriented parallel to the axis A and regularly distributed around it. The bars 53 extend between two rings 53a, 53b fixed by screws to the end walls 51, 52 and form between them lumens 54 in the axial direction.
- the end wall 52 has a central opening in which is housed a bearing 11 for the shaft 10.
- the bearing 11 comprises a sleeve housed in the central opening of the wall 52 and fixed to the latter by screwing a outer rim 1 la.
- the connection between the shaft 10 and the rotor discs is ensured by means of a part 15 fixed to the shaft 10 by screwing its central part on the end of the shaft.
- the part 15, or bowl has a plurality of branches 16 which extend parallel to the axis A.
- a jumper 17 is fixed by riveting on each branch 16. The jumpers 17 penetrate into corresponding notches formed in the inner ring of the discs 22, 24.
- the stator discs 21, 23, 25 have slots along their outer crown, separated by notches.
- the bars 53 of the housing 50 penetrate into the notches of the stator disks, immobilizing the stator disks in rotation relative to the housing.
- the latter is fixed to the bogie of the vehicle by its wall 52, by means of screws (not shown).
- the pushing structure 30 comprises a pushing piece 31 having a central part 31a forming a recess housed in the axial passage 18 surrounded by the discs and the branches 16 of the connecting piece 15.
- the central part 31a is connected to a peripheral part annular 31c of the thrust piece by a cylindrical part 3 lb_.
- the peripheral part 3c of the pushing piece is located inside the housing 50, near the end wall 51.
- each cup 32 is fixed by means of a screw 34 which applies the base 32a of the cup against the thrust piece with the interposition of a spacer 35.
- Each cup which flares towards the external face of the stator disc 21 , is supported on it by its outer edge 3212.
- the support structure 40 comprises an annular support piece 41 engaged on an internal shoulder 52â of the wall 52 of the housing and fixed by screwing thereon.
- the support piece 41 carries two sets of cups? 42, 43 arranged in pairs, with their bases 42a, 43 back to back, being regularly distributed around the axis A.
- Each pair of cups 42-43 is fixed to the part 41 by a screw 44.
- the cups 42 are supported on the outer face of the stator disc 25 by their outer edges 42b, while the cups 43 are supported on the part 41 by their outer edges 43b, with the interposition of spacers 45.
- the pneumatic actuator 60 is directly fixed to the end wall 51 of the housing 50 on the outside.
- the movable part 61 of the actuator passes through a central opening in the wall 51 and is fixed to the central part 3a of the thrust piece 31. In this way, the space requirement is reduced to a minimum, the connection between the thrust piece and the actuator extending in the passage 18. It is important to limit the transfer of the heat generated by the mutual friction of the discs 21 to 25 in the direction of the shaft 10, in particular towards the bearings inside the bearing 11 and, beyond, towards the drive members (not shown), as well as towards the actuator 60.
- a significant part of the heat is evacuated through the ventilation openings 54, at the periphery of the housing 50.
- the transfer by conduction between the rotor discs 22, 24 and the shaft 10 can be limited by making the jumpers 17 in a material which is not very conductive of heat, for example also in stainless steel.
- An additional heat shield may be provided in the form of a wall 70 whose profile has the shape desired to be housed in the space located around the shaft and delimited, on one side by the support piece 41, the wall 52 and the bearing 11 and, on the other side, by the discs and the connecting piece 15.
- the wall 70 is held in position by its peripheral edge clamped between the cups 42 and the cups 43.
- the wall 70 may consist of a sheet, for example made of stainless steel, or by several sheets spaced apart others by one or more air spaces or spaces filled with insulation.
- the wall 70 is a multiple wall formed by two sheets 71, 72 applied one against the other at the ends and forming between them an air space 73 between these ends.
- the heat transfer along the shaft 10 is limited by one or, as illustrated, several thermal barriers formed in the bearing 11.
- a first barrier is formed by an internal rim of the bearing 12 which forms a lip llb_, inside the housing 50, cooperating with a ring 74 mounted on the shaft 10 and provided with a seal 75, protecting the bearing 13.
- a second barrier formed by two rings 76, 77 with complementary profiles respectively integral with the shaft 10 and the sleeve 11 and imposing a tortuous path in the air.
- two rings 78, 79 in addition to keeping the bearing 14 in its housing, have parts with complementary profiles which still require the air to follow a tortuous path.
- FIGS. 3 and 4 illustrate another embodiment of a friction device for motor bogie brake.
- the common elements between this embodiment and that of FIGS. 1 and 2 bear the same reference numbers and will not be described again in detail.
- FIGS. 3 and 4 is distinguished in particular in that the actuator 60 is fixed to the end wall 52 of the housing 50 opposite that situated on the side of the thrust structure 130 and the pressure force exerted by the actuator is transmitted to the thrust structure via a mechanical lever connection.
- the pushing structure 130 comprises a pushing piece 131 having a central part 131a of tubular shape and an annular peripheral part 131b connected to the central part. Cups 32 are fixed to the peripheral part 131b as in the previous embodiment.
- the tubular part 131a can slide parallel to the axis A in a sleeve 55 housed in a central opening in the wall 51 and secured to a skirt 55â fixed on the end wall 51 of the housing 50 by screwing.
- the actuator 60 has its body 62 articulated, on the side of its rear face, around an axis 63 carried by two legs 64 fixed on an extension of the end wall 52 of the housing 50.
- the connection between the movable part 61 of the actuator and the central part 13 there of the thrust piece 131 is produced by means of two rods 65.
- the rods are articulated on pivots 67 situated in diametrically opposite locations at the front of the movable part 61 of the actuator.
- the links are articulated at the ends of a rod 68 which passes through opposite holes formed in the part 13 there of the thrust piece and extends perpendicularly to the axis A.
- the rod 68 also passes through guide lights 56 formed in the sleeve 55 parallel to the axis A.
- the links are articulated on axes 69 carried by lugs 57 secured to the sleeve 55.
- a spacer 66 strengthens the set of two links 65.
- the pivoting of the rods 65, 66 around the axes 69 causes the translational movement of the thrust piece 131, guided by the lights 56, and thereby, the application of a pressure force on the discs 21 to 25.
- the links 65, 66 by leverage, amplify the pressure generated by the actuator.
- the body 62 of the actuator pivots slightly around the axis 63.
- H can be supported by means of an articulated cradle 58 mounted on a plate 59 fixed to the end wall 52 of the housing.
- the cradle 58 has two forks 58a in which are supported lugs 62a located at diametrically opposite locations of the body 62 of the actuator, on the front side of the body.
- connection between the shaft 50 and the rotor discs 22, 24 is produced by means of a part 115, the central part of which has the shape of a frustoconical sleeve 115a force-fitted onto an end part 10a of corresponding frustoconical shape of the 'shaft 10.
- the sleeve 115a is immobilized axially by a nut 117 screwed onto the end of the shaft 10.
- the sleeve 115a is integral with a plurality of branches 116 regularly distributed around the axis A.
- the connection of the branches 116 with the rotor discs 22, 24 is achieved by means of jumpers 17 riveted on the branches 116 and penetrating into the notches of the inner ring of the discs.
- the support structure 40 with the support piece 41 and the two sets of cups 42, 43, as well as the bearing 11, with the bearings 13, 14 and the thermal barriers located along the bearing, are identical to those of the previous embodiment.
- a heat shield 170 is interposed between the disk assembly and the bearing 1 i inside the housing.
- the screen 170 is multi-walled formed of two sheets 171, 172 separated by an air space 173.
- the screen 170 is held by clamping its peripheral part between the sets of cups 42, 43. Its shape is such that 'It extends from the cups 42, 43, to the vicinity of the connecting piece 115.
- An embodiment of a friction device according to the invention used as a transmission brake for a heavy vehicle is illustrated by Figures 5 to 7.
- the transmission brake is mounted between a gearbox output shaft 202 and a transmission shaft 204 of common axis C which are linked in rotation by means of a connecting piece 206, or bowl.
- the shaft 202 is supported by a central bearing 208 provided at the outlet of the casing 210 of the gearbox and comprising a bearing 212 housed between the end portion 210â of the casing 210 and a ring 214 mounted on the shaft 202.
- the friction device comprises a set of three coaxial discs comprising a rotor disc 220 arranged between two stator discs 222, 224.
- the disc set is housed inside a fixed housing 226, between a annular thrust plate 228 and a bearing surface formed by the bottom 226a of the housing 226.
- the rotor disc of axis C has in its inner ring notches parallel to the axis C into which branches 206a formed at the periphery of the bowl 206 penetrate.
- the support of the thrust plate 228 against the external face of the stator disc 222 is produced by means of a thrust structure 230, by means of cups 232.
- the thrust structure 230 has a central part 230a in the form of ring through which the transmission shaft 204 is connected to an annular peripheral part 230 en in the form of a crown.
- Each cup 232 has a base on which the crown 230c rests. with the interposition of a spacer 235 forming a thermal barrier.
- Each cup 232 which widens in the direction of the push plate 228, bears on the latter by its outer edge.
- the housing 226 is located inside a cage formed by the box casing 210, a plate 240 forming the end wall and on which a sleeve 244 is fixed by screwing, and longitudinal members 242 parallel to the axis C on which the plate 240 is screwed.
- the sleeve 244 has a crown 244â against which the push plate 228 can come into abutment, with the interposition of a heat shield 250.
- the sleeve 244 In its central part 244h, the sleeve 244 has an axial passage for the ring 230a of the thrust structure.
- the sleeve 244 also has ventilation openings 244c.
- a pneumatic actuator 260 is mounted on a plate 246 secured to the housing 226.
- the movable part of the actuator is articulated at one end of a rod 262 in the form of a fork.
- the terminal parts of branches 262 ⁇ , 262b. of the rod are engaged on lugs 263 integral with the ring 230â of the thrust structure and diametrically opposite.
- the rod 262 is pivotally mounted on a pin 264 supported at its ends by flanges 248 carried by the sleeve 244 (see Figure 6).
- the pivoting of the rod 262 around the axis 264 causes the displacement structure to move in translation and, via the cups 232 and the thrust plate 228, the application of a pressure force on the discs 222, 220, 224 which achieves the desired braking or deceleration by the connection between the rotor disc 220 and the axes 202, 204.
- the rotational forces exerted on the bottom of the housing 226 by the stator disc 222 during braking or deceleration are taken up by bayonet connections 245 between the housing 226, at its axial end opposite the bottom, and the ring 244a of the sleeve, like the shows in detail Figure 7.
- a significant part of the heat generated by the friction is discharged through apertures 226c formed at the periphery of the housing 226 and the openings 243 between the side members 242 ( Figure 6).
- the cups 232 and the spacers 235 limit the heat transfer by conduction between the push plate 228 and the push structure 230.
- the heat shield 250 limits the heat transfer by conduction between the push plate 228 and the sleeve 244.
- the transfer by conduction between the rotor disk 220 and the bowl 206 can be limited by providing jumpers 206a with jumpers made of a weakly conductive material, as in the previous embodiments.
- the bowl 206 On the gearbox side, the bowl 206 has a skirt 206b which surrounds the bearing part 208 of the casing 210 by engaging in a central opening in the bottom of the housing 226, and thus forms a thermal barrier by imposing a tortuous path on the air between the interior of the housing 226 and the interior of the housing 210.
- the tortuous path can be completed by complementary profiles of the end of the bearing 208 and of the ring 214.
- a lip seal 215 can also be mounted at the outer end of the bearing 208.
- the heat transfer by convection can also be limited by means of a ring 213 fixed to the casing 210 and traversed practically without play by the shaft 202.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/600,943 US6318511B1 (en) | 1998-11-25 | 1999-11-23 | Disk brake with high thermal resistance |
JP2000584213A JP2002530605A (ja) | 1998-11-25 | 1999-11-23 | 高耐熱性を有するディスクブレーキ |
EP99956117A EP1049885A1 (fr) | 1998-11-25 | 1999-11-23 | Frein a disques a haute resistance thermique |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR98/14824 | 1998-11-25 | ||
FR9814824A FR2786239B1 (fr) | 1998-11-25 | 1998-11-25 | Dispositif de friction a disques a commande pneumatique pour transmission |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000031430A1 true WO2000031430A1 (fr) | 2000-06-02 |
Family
ID=9533157
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR1999/002875 WO2000031430A1 (fr) | 1998-11-25 | 1999-11-23 | Frein a disques a haute resistance thermique |
Country Status (5)
Country | Link |
---|---|
US (1) | US6318511B1 (fr) |
EP (1) | EP1049885A1 (fr) |
JP (1) | JP2002530605A (fr) |
FR (1) | FR2786239B1 (fr) |
WO (1) | WO2000031430A1 (fr) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7237665B2 (en) * | 2004-11-08 | 2007-07-03 | Borgwarner Inc. | Thermal energy transfer limited rotating shaft for a pneumatic fan drive system |
FR2882406B1 (fr) * | 2005-02-21 | 2007-05-04 | Stephanois Rech Mec | Ensemble d'articulation, notamment pour tringlerie de freins de bogies |
US8776955B2 (en) * | 2007-02-02 | 2014-07-15 | Warner Electric Technology Llc | Liquid cooled brake with support columns |
US8813936B2 (en) * | 2008-07-25 | 2014-08-26 | Eaton Corporation | Force transmitting assembly |
DE102009013894A1 (de) * | 2009-03-19 | 2010-10-14 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Nass laufende Lamellenbremse |
US9023112B2 (en) | 2011-02-24 | 2015-05-05 | Depuy (Ireland) | Maintaining proper mechanics THA |
US8919514B2 (en) | 2012-03-28 | 2014-12-30 | Eaton Corporation | Floating housing force transmitting assembly |
US10274034B2 (en) | 2017-07-12 | 2019-04-30 | Goodrich Corporation | Wear liner with integrated torque button |
US10941823B2 (en) | 2017-11-27 | 2021-03-09 | Goodrich Corporation | Segmented wear liner |
CN113775674A (zh) * | 2021-09-30 | 2021-12-10 | 徐州工程学院 | 一种减速装置 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE9400821U1 (de) * | 1994-01-19 | 1994-03-10 | Ortlinghaus Werke Gmbh | Vorrichtung zur Dauerbremsung einer rotierenden Welle in Prüfständen, Abrolleinrichtungen o.dgl. |
FR2697218A1 (fr) * | 1992-10-26 | 1994-04-29 | Alsthom Gec | Système de freinage pour véhicule ferroviaire utilisant des matériaux à base de carbone. |
WO1997025548A2 (fr) * | 1996-01-12 | 1997-07-17 | Mcdonnell Douglas Corporation | Dispositif retenu de freinage pour avion |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4102438A (en) * | 1976-10-18 | 1978-07-25 | The Dolphin Brake Corp. | Disc brake assembly |
US4727970A (en) * | 1984-06-12 | 1988-03-01 | Luk Lamellen Und Kupplungsbau Gmbh | Torque transmitting and torsion damping apparatus for use in motor vehicles |
US5058712A (en) * | 1989-07-07 | 1991-10-22 | American Standard Inc. | Pre-loading pivotal pin connection for a disc brake assembly |
US5538109A (en) * | 1990-12-04 | 1996-07-23 | The B. F. Goodrich Company | Piston head for an aircraft brake and insulator |
US5651430A (en) * | 1992-03-31 | 1997-07-29 | Rancourt; Claude | Disc brake assembly |
US5671827A (en) * | 1995-11-07 | 1997-09-30 | Demetriou; Ikaros | Air disc brake |
SE509044C2 (sv) * | 1995-11-29 | 1998-11-30 | K S Technology Hb | Anordning vid broms |
FR2755094B1 (fr) * | 1996-10-31 | 1998-11-27 | Messier Bugatti | Agencement de disques de frein en carbone pour unite de freinage d'aeronef, et procede d'assemblage de disques selon un tel agencement |
-
1998
- 1998-11-25 FR FR9814824A patent/FR2786239B1/fr not_active Expired - Fee Related
-
1999
- 1999-11-23 WO PCT/FR1999/002875 patent/WO2000031430A1/fr not_active Application Discontinuation
- 1999-11-23 JP JP2000584213A patent/JP2002530605A/ja not_active Withdrawn
- 1999-11-23 EP EP99956117A patent/EP1049885A1/fr not_active Withdrawn
- 1999-11-23 US US09/600,943 patent/US6318511B1/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2697218A1 (fr) * | 1992-10-26 | 1994-04-29 | Alsthom Gec | Système de freinage pour véhicule ferroviaire utilisant des matériaux à base de carbone. |
DE9400821U1 (de) * | 1994-01-19 | 1994-03-10 | Ortlinghaus Werke Gmbh | Vorrichtung zur Dauerbremsung einer rotierenden Welle in Prüfständen, Abrolleinrichtungen o.dgl. |
WO1997025548A2 (fr) * | 1996-01-12 | 1997-07-17 | Mcdonnell Douglas Corporation | Dispositif retenu de freinage pour avion |
Also Published As
Publication number | Publication date |
---|---|
EP1049885A1 (fr) | 2000-11-08 |
JP2002530605A (ja) | 2002-09-17 |
FR2786239B1 (fr) | 2001-02-16 |
US6318511B1 (en) | 2001-11-20 |
FR2786239A1 (fr) | 2000-05-26 |
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