WO2003056204A1 - Frein a disque electromecanique a autorenforcement a garniture partielle presentant un meilleur guidage de garniture de friction - Google Patents

Frein a disque electromecanique a autorenforcement a garniture partielle presentant un meilleur guidage de garniture de friction Download PDF

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Publication number
WO2003056204A1
WO2003056204A1 PCT/EP2002/014781 EP0214781W WO03056204A1 WO 2003056204 A1 WO2003056204 A1 WO 2003056204A1 EP 0214781 W EP0214781 W EP 0214781W WO 03056204 A1 WO03056204 A1 WO 03056204A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
pressure plate
disc
friction lining
brake disc
Prior art date
Application number
PCT/EP2002/014781
Other languages
German (de)
English (en)
Inventor
Martin Schautt
Antonio Pascucci
Henry Hartmann
Original Assignee
Estop 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 Estop Gmbh filed Critical Estop Gmbh
Priority to AU2002367191A priority Critical patent/AU2002367191A1/en
Priority to EP02805775A priority patent/EP1458988A1/fr
Publication of WO2003056204A1 publication Critical patent/WO2003056204A1/fr

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
    • F16D65/14—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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T2270/00—Further aspects of brake control systems not otherwise provided for
    • B60T2270/83—Control features of electronic wedge brake [EWB]
    • 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
    • F16D2123/00—Multiple operation 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
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/66—Wedges
    • 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
    • F16D2127/10—Self-amplifying or de-amplifying mechanisms having wedging elements

Definitions

  • the invention relates to self-energizing electromechanical partial brake disc brakes, in particular for motor vehicles.
  • an electric actuator applies an actuating force that applies the brake lining or friction linings to the rotating brake disk.
  • a self-energizing device in the form of a wedge arrangement uses the kinetic energy contained in the rotating brake disc to further feed the friction linings, i.e. the friction linings are pressed against the brake disc with a force which is significantly higher than the actuator force and which is not applied by the electrical actuator.
  • the basic principle of such a brake is known from German patent 198 19 564.
  • an electromechanical partial brake disc brake that combines the principle of self-energizing by means of a wedge arrangement with the compact, well-proven type of disc brakes that have a caliper that spans the brake disc and in which the friction path does not change during braking.
  • Brakes of this type are designed as fixed caliper brakes or as floating caliper brakes.
  • the invention has for its object to provide a partial brake disc brake that takes into account the previously specified request.
  • the disk brake according to the invention which is particularly suitable for use in motor vehicles, has a wedge arrangement with a wedge arrangement with a pressure plate acting directly on a friction lining and an abutment interacting with the pressure plate for self-amplification of the actuating force introduced into the brake.
  • the abutment is fixed with respect to movements in a plane parallel to the brake disc, while the pressure plate can be displaced in the circumferential direction of the brake disc relative to the abutment. The movement of the pressure plate in the circumferential direction of the brake disk leads to the delivery of the brake.
  • a plurality of first raceways extending in the circumferential direction of the brake disk are embedded in the pressure plate, each of which has a lowest point and two ramps extending in the circumferential direction of the brake disk opposite from this lowest point.
  • a second raceway is formed which is analogous to the first raceway.
  • Each pair of a first raceway and an associated second raceway forms a receptacle for a rolling element which is arranged between every first raceway and every second raceway.
  • Brake disc rotating in the main direction of rotation have a rise angle corresponding to the wedge angle ⁇ of a conventional wedge arrangement.
  • the term “main direction of rotation” here means the direction of rotation of the brake disk in which the brake disk usually rotates.
  • the main direction of rotation is the forward rotation because the forward drive corresponds to the most common driving state of a vehicle by far.
  • the described arrangement of first and second raceways with rolling elements located between them causes a helical feed movement, ie the friction lining of the disc brake according to the invention does not move tangentially to the brake disc when braking, but in the circumferential direction of the brake disc, ie it follows the ring shape of the brake disc exactly.
  • the friction path ie an imaginary track that the friction lining would leave on the brake disc surface during the braking process, does not change in the brake according to the invention, regardless of how hard the brakes are applied.
  • the design of a disc brake according to the invention can therefore be just as compact as that of a conventional fixed or floating caliper disc brake without a self-boosting device. If necessary in the
  • the wedge angle ⁇ is decisive for the degree of self-reinforcement.
  • the wedge angle is the angle at which the interacting wedge surfaces of the pressure plate and abutment are arranged with respect to a plane (e.g. the brake disc surface) to which the force is to be transmitted.
  • the disc brake according to the invention does not use a linear wedge arrangement, but rather one in which the pressure plate and the abutment are rotated helically against one another in order to advance the friction lining, i.e. to move towards the brake disc.
  • the ramps mentioned which are embedded in the pressure plate and the abutment, are consequently helical ramps for which the ratio ⁇ between the angle of rotation ⁇ related to the axis of rotation of the brake disc and the infeed path x has a defined value.
  • the effective brake disc radius r we k is the radius at which an idealized friction force F R must act at one point in order to generate the same friction torque M R as the real friction force F R that acts flat on the friction lining surface.
  • the effective brake disc radius is calculated M ⁇ r - ⁇ - p N - dA F R ⁇ ⁇ - p N - dA
  • R radius of the surface element considered
  • the wedge angle can remain the same over the entire delivery path, but it can also change depending on the delivery path.
  • the wedge angle ⁇ decreases with increasing feed path. In this way, in extreme situations, i.e. with a minimum coefficient of friction and a very high required friction or braking torque, the level of self-amplification increases without the brake getting stuck in normal situations due to an excessively high degree of self-amplification.
  • the ramps responsible for delivering the friction lining when braking a brake disk rotating counter to the main direction of rotation can have the same wedge angle ⁇ as those already mentioned, for delivering the friction lining when braking the brake disk rotating in the main direction of rotation. ramps.
  • the lower degree of self-amplification at a larger wedge angle can be tolerated, since the braking torque required for braking the brake disk rotating counter to the main direction of rotation is usually significantly lower.
  • any type of rolling element is suitable for use in the disc brake according to the invention.
  • the rolling elements are balls.
  • the raceways in the pressure plate and the abutment have an at least approximately semicircular cross section, so that the ball rolling in the raceway touches the raceway in a linear manner and not only in a punctiform manner.
  • the rolling elements are cylindrical rollers.
  • two cylindrical rollers are preferably arranged next to one another along a common cylindrical roller axis in each rolling element receptacle.
  • the rolling behavior of two short cylindrical rollers arranged side by side is significantly more favorable than the rolling behavior of a continuous cylindrical roller of corresponding length, since the difference in the rolling radii between the radially inner and the radially outer end of a short cylindrical roller is smaller. The proportion of sliding friction is thereby reduced, rolling friction predominates.
  • the rolling elements In order to ensure a synchronous movement of the rolling elements, they can be guided by means of a cage. Furthermore, springs or similar means can be provided which ensure permanent contact between the rolling elements (regardless of their shape) and the raceways.
  • the radial guidance of the two cylindrical rollers is preferably carried out on the outside by a collar of the pressure plate that laterally delimits the first raceway and on the inside by a web that is between the two cylindrical rollers is arranged and extends from the abutment into the rolling element receptacle.
  • At least one friction lining is actuated directly in the brake according to the invention as already mentioned.
  • Disc brake an electric actuator with two electric motors, the rotary movement of which is transmitted to the pushing plate of the pressure plate in the circumferential direction of the brake disc via a spindle drive on the pressure plate.
  • An electric motor is arranged on one side of the pressure plate and the other electric motor on the opposite side of the pressure plate.
  • An electrical actuator designed in this way enables the pressure plate to be positioned without play, regardless of whether the wedge arrangement is currently acting as a tension wedge or as a pressure wedge.
  • the abutment is supported on a brake caliper which overlaps the brake disk and which, during a braking operation, presses another friction lining against the other side of the brake disk (floating caliper principle).
  • the abutment can be moved to and from the brake disc with the brake caliper.
  • At least the ramps responsible for delivering the friction lining when the brake disc rotating in the main direction of rotation is braked are shaped such that during the infeed process, i.e. when the friction lining moves towards the brake disc surface, the pressure plate not only moves towards the brake disc, but is also tilted relative to the brake disc surface. In this way, a misalignment of the friction lining caused by an expansion of the brake caliper is counteracted, and it can be ensured that the friction lining surface always comes into contact with the brake disk surface in exactly parallel fashion. An uneven distribution of the contact pressure and an uneven wear of the friction lining is avoided.
  • the degree of tilting of the pressure plate described above preferably increases with increasing angle of rotation between the pressure plate and the abutment, in order in this way to compensate for the widening of the brake caliper which increases with increasing braking torque.
  • FIG. 2 is a view similar to FIG. 1 with the brake caliper and abutment removed
  • FIG. 3 shows a view of the brake from FIG. 1 in a spatial representation obliquely from below with the pressure plate hidden
  • FIG. 4 shows the view from FIG. 1 with the brake in the braking position for a brake disk rotating in the main direction of rotation
  • FIG. 5 shows the view from FIG. 1 with the brake in the braking position for a brake disk rotating counter to the main direction of rotation
  • FIG. 6a-6c detailed views of the wedge arrangement with the brake released (FIG. 6a), braking in the main direction of rotation (FIG. 6b), and braking against the main direction of rotation (FIG. 6c),
  • Fig. 7a - 7c views corresponding to Fig. 6a to 6c for a modified, second embodiment
  • Fig. 1 shows schematically an electromechanical generally designated 10
  • the housing 12 of the brake 10 is shown in broken lines in FIG. 1 in order to allow a view of the components arranged in the housing 12.
  • the housing 12 is provided for attachment to a component fixed to the vehicle, for example for attachment to a steering knuckle (not shown).
  • the brake 10 is assigned a brake disc 14 which is rotatable about an axis A and which is connected in a rotationally fixed manner to a component to be braked, for example to a vehicle wheel (not shown).
  • a floating caliper 16 is slidably guided on the housing 12 of the brake 10 parallel to the axis of rotation A of the brake disc 14.
  • the floating caliper 16 engages over the brake disc 14 and acts with each of its two arms 16a and 16b on a brake pad 18 and 20.
  • Each brake pad 18, 20 consists of a friction lining 18a, 20a and a carrier plate on which the friction lining 18a, 20a is fastened, for example by gluing. Only the carrier plate 20b is shown in the figures.
  • a wedge arrangement 22 is present between the vehicle-internal brake pad 18 and the associated arm 16a of the floating caliper 16, which serves to self-amplify the actuating force introduced into the brake 10.
  • the most important components of the wedge arrangement 22 are a pressure plate 24, which acts directly on the brake pad 18, and an abutment 26, on one side of which the arm 16a of the floating caliper 16 acts and on the opposite side of which the pressure plate 24 is supported. Both the pressure plate 24 and the abutment 26 have a circular segment shape.
  • the pressure plate 24 can also be directly connected to the friction lining 18a, for example by gluing, and thus also take over the function of the carrier plate.
  • first raceways 28 which each have a deepest point P and two ramps 30, 32 extending in opposite directions, are embedded in the surface of the pressure plate 24 facing the abutment 26 include.
  • four first raceways 28 are present, but more or fewer first raceways 28 may be present in the case of modified exemplary embodiments which are not shown.
  • second raceways 34 which are designed analogously to the first raceways 28, are let in at locations which lie opposite the first raceways 28.
  • Each pair of a first raceway 28 and an associated second raceway 34 forms a receptacle for a rolling element, which is arranged between each first raceway 28 and every second raceway 34 and rolls or rolls in the receptacles formed by the raceways 28, 34 can pass on.
  • the rolling elements are balls 36.
  • the profile of the raceways 28 and 34 is adapted to the rolling elements used, ie the raceways 28 and 34 of the first exemplary embodiment shown in FIGS. 1 to 6 have one of the balls 36 adjusted cross sectional contour.
  • the contact of each ball 36 in the raceways 28, 34 is thus linear and not only punctiform, which improves the guidance of the balls 36 and reduces the material load occurring in the receptacles.
  • the figures show four recordings, each with one arranged therein
  • Ball 36 At least three recordings with a ball are required for geometrically determined guidance. However, clearly more than four balls can be used (in corresponding images), and the number of balls can be even or odd. The general rule is that more balls equalize the load on the wedge arrangement 22 and increase the load capacity of the wedge arrangement as a whole. Each ball 36 represents a force application point, and many force application points reduce the internal stiffness requirement of the pressure plate 24 and abutment 26 so that these parts can be made easier.
  • An electric actuator which in the exemplary embodiment shown is formed by two linear actuators 38, 40, serves to actuate the disc brake 10.
  • Each linear actuator 38, 40 has an electric motor 42, 42 'with an integrated spindle nut and a rotation angle sensor and a push rod 44, 44' designed as a spindle.
  • Ball joints 46, 46 'and 48, 48' couple the linear actuators 38, 40 on the one hand to the housing 12 of the brake 10 and on the other hand to the pressure plate 24.
  • the pressure plate 24 By actuating the two electric motors 42, 42 ', the pressure plate 24 can be moved back and forth along a circular path following the brake disc 14.
  • the structure described consisting of pressure plate 24, abutment 26 and receptacles arranged therebetween with balls 36 therein, forms a ball ramp arrangement for self-reinforcing the actuating force introduced into the brake, in which the pressure plate 24 can be rotated in the angular direction ⁇ relative to the abutment 26.
  • the raceways 28, 34 are designed so that for the path of the center of gravity of the inner friction lining 18a between the movement component tangential to the brake disc and the movement component in the feed direction x, which is parallel to the axis of rotation A, there is a ratio of tan ⁇ , where ⁇ is the for self-energizing brakes is typical wedge angle ⁇ .
  • the pressure plate 24 is displaced in the direction of rotation of the brake disc 14 by means of the two linear actuators 38, 40.
  • the balls 36 run from their starting positions shown in FIG. 6a, in which they rest at the lowest point P of each raceway 28, 34, up the ramps 30 (see FIG. 6b), as a result of which the pressure plate 24 and with it the brake pad 18 are moved in the direction of rotation of the brake disk 14 and at the same time in the direction x toward the brake disk surface (delivery phase).
  • the wedge arrangement 22 ensures that part of the kinetic energy contained in the rotating brake disc 14 is converted into a feed force that is normal to the surface of the brake disc, so that the two linear actuators 38, 40 only a small part of that required Braking torque required delivery force must apply.
  • 4 shows the brake 10 in the applied state for braking a brake disk 14 rotating in the main direction of rotation.
  • the friction linings 18a, 20a face each other exactly in this tightened state, while in the released state (see FIG. 1) they have an angular offset to one another.
  • the actuation of the linear actuators 38, 40 is carried out by an electronic control unit (not shown), which compares a friction force measured by a sensor (not shown) with a predetermined friction force setpoint and any
  • the control positions the pressure plate 24 by means of the two linear actuators 38, 40 in such a way that the desired frictional force is maintained even when the coefficient of friction fluctuates.
  • the two linear actuators 38, 40 which can be controlled independently of one another, enable the pressure plate 24 to be positioned without play: at low required actuation forces, ie in areas in which the coefficient of friction ⁇ corresponds to the tan ⁇ , the two linear actuators 38, 40 act against one another and thus eliminate any play. If larger actuation forces are required, which is the case if the value of the friction coefficient ⁇ deviates strongly from tan ⁇ , one of the linear actuators 38, 40 is reversed so that the actuation forces of both actuators 38, 40 add up.
  • the linear actuators 38, 40 move the pressure plate 24 again in the direction of rotation of the brake disk 14, but now in the opposite direction to the previously described braking (see FIG. 6c).
  • the balls 36 move up the ramps 32, which may have the same or a different pitch angle as the ramps 30. 5 shows the brake 10 in the locked position when the brake disk 14 rotating counter to the main direction of rotation is braked.
  • An adjusting device can move the abutment 26 parallel to the axis of rotation A of the brake disc 14 in order to compensate for the friction lining wear that occurs during operation of the brake 10.
  • FIGS. 7 and 8 show a second exemplary embodiment of the wedge arrangement 22, in which instead of balls 36 cylindrical rollers are used, which are arranged in appropriately adapted receptacles.
  • two cylindrical rollers 52, 54 are arranged alongside one another along a common cylindrical roller axis Z in each receptacle formed from a first raceway 28 'and a second raceway 34'.
  • the radial guidance of the two cylindrical rollers 52, 54 takes place on the outside thereof by a respective collar 56, 58 laterally delimiting the first raceway 28 ', which in the exemplary embodiment shown is formed in one piece with the pressure plate 24, and on the inside by a web 60 which is formed on the abutment 26 in the second raceway 34 'and extends into the receptacle between the two cylindrical rollers 52, 54 (see FIG. 8).
  • the function of the wedge arrangement 23 according to the second embodiment corresponds to the function illustrated in Fig. 6, i.e. for braking a brake disk 14 rotating in the main direction of rotation, the cylindrical rollers 52, 54 run up the ramps 30 'from their starting position shown in FIG. 7a (see FIG. 7b), while for braking a brake disk 14 rotating in the opposite direction of rotation, the ramps 32 'can be used (see Fig. 7c).
  • the ramps 30 in particular can be shaped such that the pressure plate 24 not only moves toward the brake disk 14 during the infeed process, but is also tilted relative to the brake disk plane.
  • the misalignment of the friction lining 18a caused by an expansion of the brake caliper 16 at high application forces can be achieved are counteracted, ie the friction lining surface is always kept parallel to the brake disc surface.
  • the degree of tilting of the pressure plate 24 increases with an increasing angle of rotation between the pressure plate 24 and the abutment 26, in order in this way to take into account a widening of the brake caliper 16 that increases with the application force.

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

Abstract

La présente invention concerne un frein à disque électromécanique à autorenforcement à garniture partielle (10) présentant un disque de frein rotatif (14), un actionneur électrique produisant une force de commande et une garniture de friction (18a) actionnée par ledit actionneur électrique et conçue pour venir en contact avec une face du disque de frein (14). Ledit actionneur électrique agit par un dispositif de clavette (22) sur cette garniture de friction (18a) pour la régler à un angle de clavette ( alpha ). Afin d'améliorer le guidage de la garniture de friction, le dispositif de clavette (22) présente une plaque de compression (24) qui agit sur la garniture de friction (18a) et une butée (26) qui coopère avec cette plaque. Ladite plaque de compression (24) peut tourner en direction périphérique du disque de frein par rapport à ladite butée (26). La plaque de compression (24) présente plusieurs premières voies de roulement (28) qui s'étendent en direction périphérique du disque de frein (14). Chaque première voie de roulement (28) comprend un point inférieur (P) et deux rampes (30, 32) s'étendant dans des directions opposées par rapport au point inférieur. La butée (26) présente une seconde voie de roulement (34), identique aux premières voies de roulement (28), face à chaque première voie de roulement (28) de la plaque de compression (24). Chaque paire constituée d'une première voie de roulement (28) et d'une seconde voie de roulement associée (34) forme un logement destiné à un corps de roulement se trouvant entre les voies de roulement (28, 34). Au moins les rampes (30) conçues pour régler la garniture de friction (18a) lors d'un freinage du disque de frein (14) tournant dans un sens de rotation principal présentent un angle de montée qui correspond à l'ange de clavette ( alpha ).
PCT/EP2002/014781 2001-12-28 2002-12-27 Frein a disque electromecanique a autorenforcement a garniture partielle presentant un meilleur guidage de garniture de friction WO2003056204A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2002367191A AU2002367191A1 (en) 2001-12-28 2002-12-27 Self-reinforcing electromechanical partially lined disc brake with improved friction lining guidance
EP02805775A EP1458988A1 (fr) 2001-12-28 2002-12-27 Frein a disque electromecanique a autorenforcement a garniture partielle presentant un meilleur guidage de garniture de friction

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10164317.9 2001-12-28
DE2001164317 DE10164317C1 (de) 2001-12-28 2001-12-28 Selbstverstärkende elektromechanische Teilbelagscheibenbremse mit verbesserter Reibebelagführung

Publications (1)

Publication Number Publication Date
WO2003056204A1 true WO2003056204A1 (fr) 2003-07-10

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Country Status (4)

Country Link
EP (1) EP1458988A1 (fr)
AU (1) AU2002367191A1 (fr)
DE (1) DE10164317C1 (fr)
WO (1) WO2003056204A1 (fr)

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WO2005015046A1 (fr) * 2003-08-07 2005-02-17 Robert Bosch Gmbh Frein a disque electromecanique a amplification automatique
WO2005061920A1 (fr) 2003-12-24 2005-07-07 Robert Bosch Gmbh Frein a friction electromecanique a auto-amplification
WO2005064195A1 (fr) 2003-12-24 2005-07-14 Robert Bosch Gmbh Frein a friction electromecanique a auto-amplification
WO2007000410A1 (fr) * 2005-06-27 2007-01-04 Haldex Brake Products Ab Frein a disque
WO2007023051A1 (fr) * 2005-08-24 2007-03-01 Robert Bosch Gmbh Frein a friction auto-amplificateur
WO2007115900A1 (fr) * 2006-04-04 2007-10-18 Robert Bosch Gmbh Frein à disque à garniture partielle électromécanique à auto-amplification
WO2008037602A1 (fr) * 2006-09-28 2008-04-03 Continental Automotive Gmbh Entraînement sans jeu pour un dispositif de freinage électromagnétique
JP2012061977A (ja) * 2010-09-16 2012-03-29 Kubota Corp 作業車
EP4098903A1 (fr) * 2021-06-01 2022-12-07 Huawei Digital Power Technologies Co., Ltd. Appareil de freinage et automobile

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DE102005049760C5 (de) * 2005-10-18 2009-10-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Selbstverstärkende Scheibenbremse mit elektromechanischem Aktuator
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DE102006001621A1 (de) * 2006-01-11 2007-07-19 Voith Turbo Gmbh & Co. Kg Schaltbarer Freilauf und Leistungsübertragungseinheit mit schaltbarem Freilauf
DE102006003749A1 (de) * 2006-01-26 2007-08-09 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse in selbstverstärkender Bauart
DE102006034848A1 (de) * 2006-07-27 2008-01-31 Siemens Ag Schnurbremse
DE102007003497A1 (de) 2007-01-24 2008-07-31 Siemens Ag Gurtaufroller
DE102007027867A1 (de) 2007-06-18 2008-12-24 Continental Automotive Gmbh Verfahren und Anordnung zur Ansteuerung zumindest einer elektromechanischen Bremsaktuatoreinheit einer Türbremseinrichtung
DE102008017182B4 (de) * 2008-04-04 2016-05-12 Trw Automotive Gmbh Mechatronisches Fahrzeuginsassen-Rückhaltesystem
DE102017203934B4 (de) 2017-03-09 2021-04-29 Continental Teves Ag & Co. Ohg Vollscheibenbremse

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WO2005015046A1 (fr) * 2003-08-07 2005-02-17 Robert Bosch Gmbh Frein a disque electromecanique a amplification automatique
CN100394058C (zh) * 2003-08-07 2008-06-11 罗伯特·博世有限公司 具有自行增力的机电式盘式制动器
WO2005061920A1 (fr) 2003-12-24 2005-07-07 Robert Bosch Gmbh Frein a friction electromecanique a auto-amplification
WO2005064195A1 (fr) 2003-12-24 2005-07-14 Robert Bosch Gmbh Frein a friction electromecanique a auto-amplification
US7735613B2 (en) 2003-12-24 2010-06-15 Robert Bosch Gmbh Self-boosting electromechanical friction brake
WO2007000410A1 (fr) * 2005-06-27 2007-01-04 Haldex Brake Products Ab Frein a disque
WO2007023051A1 (fr) * 2005-08-24 2007-03-01 Robert Bosch Gmbh Frein a friction auto-amplificateur
WO2007115900A1 (fr) * 2006-04-04 2007-10-18 Robert Bosch Gmbh Frein à disque à garniture partielle électromécanique à auto-amplification
US8827053B2 (en) 2006-04-04 2014-09-09 Robert Bosch Gmbh Self-amplifying electromechanical partial lining disc brake
WO2008037602A1 (fr) * 2006-09-28 2008-04-03 Continental Automotive Gmbh Entraînement sans jeu pour un dispositif de freinage électromagnétique
JP2012061977A (ja) * 2010-09-16 2012-03-29 Kubota Corp 作業車
EP4098903A1 (fr) * 2021-06-01 2022-12-07 Huawei Digital Power Technologies Co., Ltd. Appareil de freinage et automobile

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EP1458988A1 (fr) 2004-09-22
DE10164317C1 (de) 2003-10-09

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