WO2003106857A1 - Frein, notamment frein a disque a amplification automatique et angle d'attaque variable - Google Patents

Frein, notamment frein a disque a amplification automatique et angle d'attaque variable Download PDF

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Publication number
WO2003106857A1
WO2003106857A1 PCT/DE2003/000989 DE0300989W WO03106857A1 WO 2003106857 A1 WO2003106857 A1 WO 2003106857A1 DE 0300989 W DE0300989 W DE 0300989W WO 03106857 A1 WO03106857 A1 WO 03106857A1
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WO
WIPO (PCT)
Prior art keywords
brake
friction
support
disc
force
Prior art date
Application number
PCT/DE2003/000989
Other languages
German (de)
English (en)
Inventor
Andreas Henke
Willi Nagel
Dirk Hofmann
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2003106857A1 publication Critical patent/WO2003106857A1/fr

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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
    • 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
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/04—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by moving discs or pads away from one another against radial walls of drums or cylinders
    • F16D55/14—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by moving discs or pads away from one another against radial walls of drums or cylinders with self-tightening action, e.g. by means of coacting helical surfaces or balls and inclined surfaces
    • 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
    • F16D2121/02—Fluid pressure
    • 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
    • F16D2125/58—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
    • F16D2127/007—Auxiliary mechanisms for non-linear operation
    • 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 a brake, in particular a disc brake, with the features of the preamble of claim 1.
  • Disc brakes for in particular electromechanical actuation which have a wedge mechanism in order to achieve self-amplification.
  • the known disc brakes have a brake disc as a brake body and a friction brake lining which can be displaced approximately parallel to a secant of the brake disc.
  • the friction brake lining has a wedge, via which it is supported on a support which runs at an angle to the brake disc.
  • the friction brake lining with the wedge is displaced in the direction of a narrowing space, also called a wedge gap, between the support and the brake disc.
  • the friction brake lining is pressed against the brake disc by the support and brakes it.
  • the rotating brake disc exerts a frictional force on the friction brake pad, which the Friction brake lining is applied in the direction of the narrowing space between the support and the brake disc.
  • the frictional force exerted by the rotating brake disc on the pressed-on friction brake lining increases the pressing force of the friction brake lining on the brake disc, and brake force amplification is achieved.
  • the amount of brake force boost depends on the angle between the support and the brake disc and on a coefficient of friction ⁇ .
  • the coefficient of friction ⁇ is the factor from the frictional force to the pressing force of the friction brake lining on the brake disc. It fluctuates in operation and can be assumed to be around 0.2 ... 0.6.
  • the angle between the support and the brake disc is chosen so large that blocking of the brake disc is avoided at the maximum coefficient of friction. Since the coefficient of friction ⁇ during operation is usually in a middle range between its minimum and maximum value, i.e. around 0.4, a maximum possible self-amplification is usually not used.
  • DE 100 46 177 A1 has proposed that the support of the friction brake lining be made adjustable. This makes it possible to adjust the angle between the support and the brake disc and thereby to adjust the self-reinforcement.
  • a disadvantage is the design effort for adjusting the support.
  • the basic idea of the invention is to shape the support of a brake, in particular a disc brake of the type explained in the introduction, in such a way that the self-amplification is better utilized. This is achieved with a non-adjustable support.
  • the brake according to the invention with the features of claim 1 has a support with at least two areas adjoining one another in the direction of displacement of the friction brake lining.
  • the area of the support referred to below as the first area applies to the angle ⁇ between the support and a brake body to be braked, for example a brake disc: ⁇ > arctan ⁇ m a ⁇ , where ⁇ ma ⁇ is the greatest coefficient of friction that occurs during operation.
  • This section ends when the frictional force FR between the brake lining and the brake disc at the maximum coefficient of friction ⁇ ma a maximum value fr_ ma ⁇ reached.
  • the maximum frictional force FR_m a ⁇ is fixed; for example, it is the frictional force that is required to lock a vehicle wheel in optimally grippy road conditions.
  • the limit case ⁇ arctan ⁇ m a x
  • the angle ⁇ between the support and the brake body is constant in the first area, so the support is straight.
  • the coefficient of friction ⁇ in the course of the second area of the support from the maximum value ⁇ ma ⁇ at the beginning of the second range decreases to the minimum value ⁇ m j n at the end of the second range.
  • the coefficient of friction ⁇ cannot be selected, but is given by the prevailing conditions.
  • the effect of the support shaped according to the invention is evident from the following considerations: If the coefficient of friction when the brake is actuated has the maximum value ⁇ m a x, the friction brake lining is displaced in the first region of the support, the displacement path x depending on the desired frictional force FR between the friction brake lining and the brake body , ie of the desired braking force.
  • the maximum friction force F _ ma is reached at the end point of the first area of the support.
  • a safety surcharge S can be added to the coefficient of friction ⁇ as stated above, the angle ⁇ thereby becomes larger, the self-reinforcement becomes smaller and an actuating force F app which is dependent on the height of the safety surcharge is required.
  • F R _ max is reached at the end of the first area.
  • the friction brake lining is shifted into the second area of the support in order to achieve a high friction force FR.
  • the following also applies to the prevailing coefficient of friction ⁇ , that the friction brake lining is shifted into the second area of the support at most so that the friction force F R reaches the maximum value F Rj ⁇ la x.
  • the prevailing coefficient of friction ⁇ that the self-amplification reaches its maximum value and the actuating force F app becomes zero. If the desired frictional force FR is lower, the displacement x is shorter and the friction brake lining is at a point on the support at which the angle ⁇ is larger, that is to say the self-reinforcement is smaller.
  • An actuating force F app is required to apply the frictional force FR; there is no risk of the brake disc jamming.
  • an actuating force F app is to be applied which increases with increasing friction force FR in the first area of the support and decreases again in the second area of the support.
  • the actuating force F app decreases to zero when the maximum friction force F R _ max is reached .
  • the invention has the advantage that the actuating force F app is reduced.
  • the maximum actuation force F app is achieved when the friction brake lining is at the end of the first portion of the support and the friction coefficient ⁇ value ⁇ m in the minimum has.
  • the maximum actuation force is achieved with maximum friction force and minimum coefficient of friction.
  • the invention improves the use of the self-reinforcing effect. This does not require any design effort, such as adjusting the angle of the support. It should also be borne in mind that the pressure force of the friction brake lining against the brake body is dependent on the displacement path of the friction brake lining. It is dependent on the stiffness or expansion of a brake caliper including, for example, the stiffness of the friction brake linings. A certain contact pressure of the friction brake lining against the brake body is thus established with a specific displacement path x of the friction brake lining. The actuation force required for this displacement depends not only on the angle ⁇ between the support and the brake body but also on the coefficient of friction ⁇ .
  • a certain frictional force FR does not occur with a certain actuating force F app , but a certain displacement path x of the friction brake lining causes a certain pressing force of the friction brake lining against the brake body, which in turn creates a frictional force FR between the given and possibly changing coefficient of friction ⁇ the friction brake pad and the brake disc.
  • the actuation force F app required for this displacement of the friction brake pad is dependent on the coefficient of friction ⁇ in addition to the angle ⁇ between the support and the brake body at the respective point of the support. Since the above consideration shows that the spring stiffness of the brake caliper including the friction brake linings influences the pressing force and, via these, the friction force and the actuating force, the shape of the support depends on the respective caliper.
  • the invention has been explained above with a view to a disc brake, because it can be illustrated comparatively clearly using the example of a disc brake and because a disc brake is a preferred embodiment of the invention. Nevertheless, the invention is not limited to this type of brake, but basically applicable to any friction brakes. Except on so-called claw brakes (a type of inner or double disc brake, the brake disc of which is U-shaped on the circumference and whose friction brake pads are pressed against the U-shaped circumferential edge for braking from the inside), the invention can also be used, for example Realize drum brake.
  • the brake body of the brake is a brake disc in the case of a disc brake and one in the case of a drum brake Brake drum.
  • the support In comparison to a disc brake, in the case of a drum brake, the support, in addition to its shape explained above, must be imagined curved around the radius of the brake drum.
  • the displacement of the friction brake lining (brake shoe of the drum brake) for actuating the brake takes place in an arc in the circumferential direction of the brake drum.
  • the support does not have to be fixed in place or on the caliper, but can also be part of the friction brake lining or connected to it.
  • the friction brake lining is supported via the support, for example on a stationary or brake caliper-fixed abutment.
  • This embodiment of the invention simplifies the control of the friction force F R of the brake.
  • a length of the support in the direction of displacement of the friction brake lining is shortened and a displacement path x of the friction brake lining, an adjustment time is shortened.
  • the maximum necessary actuation force F app _ max is not increased or is increased only slightly.
  • Figure 1 is a schematic representation of a disc brake according to the invention, to explain it;
  • Figure 2 shows the course of a support of the disc brake of Figure 1 in a coordinate diagram
  • FIG. 3 shows a force curve diagram belonging to FIG. 2
  • Figure 4 shows a second course of the support of the disc brake
  • FIG. 5 shows a force curve diagram belonging to FIG. 4
  • FIG. 6 shows a simplified illustration of an embodiment of a disc brake according to the invention.
  • Figure 7 is an enlarged view of a form of support of the
  • FIGS. 1 and 7 The figures are not to scale, the support in FIGS. 1 and 7 and the diagrams in FIGS. 2 to 5 are shown greatly enlarged.
  • the disk brake 10 shown schematically in FIG. 1, has a brake disk 12 as the brake body and a friction brake lining 14.
  • the friction brake pad 14 is supported on a support 16 which extends at an angle ⁇ to the brake disc 12.
  • the angle ⁇ is constant in a first region I of the support 16, the support 16 forms one in the region I. Wedge.
  • the support 16 is curved with an increasingly acute angle ⁇ to the brake disc 12. A transition from area I to area II is continuous, the angle ⁇ at the beginning of area II is equal to the angle of area I.
  • the friction brake pad 14 is displaced in a direction of rotation n of the brake disc 12.
  • the direction of displacement of the friction brake pad 14 is denoted by x.
  • an actuating force F app in the direction of displacement x must be exerted on the friction brake pad 14. Since the support 16 extends at an angle ⁇ at an angle to the brake disc 12, the friction brake lining 14 moves transversely to the brake disc 12 due to the displacement thereof, or the friction brake lining 14 presses the support 16 away from the brake disc 12.
  • the transverse displacement of the friction brake lining 14 is denoted by y in FIG. 1.
  • the friction force FR is the product of the coefficient of friction ⁇ , which can fluctuate between approximately 0.2 and 0.6 during operation, and the normal force F.
  • a spring 18 is shown above the support 16, via which the support 16 is supported in a brake caliper 20.
  • the spring 18 is intended to symbolize an elasticity of the disc brake 10, in particular an elastic expansion of the brake caliper 20, an elastic compression of the friction brake pad 14 and any other elasticities.
  • Such elasticities which cannot be avoided in practice, can be assumed for a theoretical consideration as being replaced by the spring 18 with the spring stiffness C and the brake caliper 20 can be regarded as rigid.
  • the support 16 is supported with low friction by rollers 22 on the brake caliper 20.
  • the normal force F with which the friction brake pad 14 is pressed against the brake disc 12 is equal to the product of the expansion of the brake caliper 20 and the spring stiffness C of the spring 18, wherein the expansion of the brake caliper 20 can be equated with the transverse displacement y of the friction brake pad 14, with the zero point the transverse displacement y at the point where the friction brake pad 14 just comes to rest on the brake disc 12.
  • the frictional force FR between the friction brake lining 14 and the brake disc 12 brakes the brake disc on the one hand 12.
  • reduces the frictional force FR the app in the direction of the actuating force F acting on the friction brake lining 14 acts, app the force required to move the friction brake lining 14 operating force F.
  • the frictional force FR causes the disc brake 10 to self-amplify, the self-reinforcement depending in particular on the angle ⁇ between the support 16 and the brake disc 12 and on the coefficient of friction ⁇ between the friction brake lining 14 and the brake disc 12.
  • the angle ⁇ in the region II of the support 16 changes with increasing displacement of the friction brake lining 14 and the coefficient of friction ⁇ can change during operation.
  • the basic idea of the invention is to design the support 16 in the region II in such a way that the actuating force F app becomes zero when a maximum friction force F R _ m ax to be specified is reached.
  • the result is the profile of the support 16, which is enlarged and not shown to scale in FIG. 2.
  • FIG. 3 shows selected profiles of the actuating force F app for selected coefficients of friction ⁇ .
  • the invention becomes clear when one understands the displacement of the friction brake lining 14, the actuation force F app required for this and the friction force FR achieved thereby at selected friction values ⁇ .
  • the maximum friction force F R _ max selected is the friction force that is required to lock a vehicle wheel in optimally grippy road conditions.
  • the self-amplification of the disc brake 10 is so great that the actuating force F app becomes zero when the maximum friction force F R _ max is reached. For a lower friction force FR, the displacement of the friction brake pad 14 is smaller.
  • the course of the operating force F app with minimal friction coefficient ⁇ m i n is designated in Figure 3 ⁇ m in. It can be seen that the actuating force F app increases from zero straight to the end of area I of the support 16 and decreases degressively in area II to zero when the maximum friction force F R _ max is reached. For comparison, the course of the actuating force F app is shown with a broken line in a straight support with a constant angle ⁇ over its entire length, that is, with a wedge as a support. The straight line is labeled "wedge" and the assumed coefficient of friction ( ⁇ min) is given.
  • the displacement of the friction brake lining 14 is shortened to achieve the maximum friction force F R _ m a m , but the actuation force F app _m ax required to achieve the maximum friction force F _ ma _ is three times as large as in the disk brake 10 according to the invention is.
  • the factor 3 results from a ratio of the maximum to the minimum coefficient of friction ⁇ max / ⁇ m in of 3, since a wedge must be designed for the maximum coefficient of friction ⁇ ma ⁇ in order to prevent the disc brake 10 from locking.
  • the shape of the support 16 is for different disc brakes 10 with different brake calipers 20 and friction brake pads 14 different.
  • ⁇ arctan ⁇ ma ⁇
  • support 16 is a wedge in area I
  • the angle is constant.
  • the angle can also be greater than arctan ⁇ ma ⁇ , so support 16 in area I can also be designed as a curve.
  • Figure 4 shows a different course of the support 16 than Figure 2.
  • the support 16 is shaped in the area II so that the actuating force F ap remains constant until the maximum friction force F R _ ma is reached or increases slightly due to better controllability.
  • the corresponding profiles of the operating force F APP are for different friction coefficients ⁇ m i n, ⁇ ⁇ ma, ⁇ shown in FIG. 5
  • the support 16 is more curved in area II, the displacement path of the friction brake pad 14 is somewhat shorter.
  • the maximal Operating force F app _max to be applied with a minimum coefficient of friction ⁇ m i n is the same as in Figures 2 and 3 provided that the support 16 is formed so that the operating force F app remains constant in the region II. If the actuating force F app increases in area II, the maximum actuating force F app _ m ax is somewhat larger than in FIGS. 2 and 3.
  • FIG. 6 shows a schematic and simplified illustration of an embodiment of a disc brake 10 according to the invention.
  • a brake caliper 20 there are two friction brake linings 14, 24, one of which has a friction brake lining 14 which can be displaced in the direction of a brake disc 12 and the other 24 of which is immovable.
  • an electric motor 26 is provided, which displaces the friction brake lining 14, for example via a spindle drive 28.
  • the spindle drive 28 is shown symbolically in FIG. 6 as a spindle.
  • the displaceable friction brake lining 14 is supported on rollers 16 on supports 16 of the brake caliper 20.
  • the supports 16 are shaped to match, they are designed as explained above for FIGS. 1 to 5.
  • the course of one of the two supports 16 is greatly enlarged in FIG. 7 and is not shown to scale.
  • the supports 16 of the disc brake 10 are mirror images.
  • the disc brake 10 is therefore equally suitable for both directions of rotation of the brake disc 12, the friction brake pad 14 is always shifted in the actual direction of rotation of the brake disc 12.
  • the support 16 In front of the area I, the support 16 has an area labeled 0 with a large angle ⁇ . In this area 0, an air gap, ie a gap between the friction brake linings 14, 24 and the brake disc 12, is overcome.
  • a displacement limit 32 for the friction brake lining 14 can be connected to the area II. However, this is not necessary.
  • the support 16 has a length in the direction of displacement of, for example, 6 mm in each direction of rotation and an increase transversely to the brake disc 12 of, for example, 2 mm.
  • the disc brake 10 shown in FIG. 6 has a wear adjustment device 36 for the clearance.
  • the wear adjustment device 36 is shown in the drawing as a rotatable eccentric element.
  • the wear adjustment device 36 is preferably designed to adjust itself automatically. Such wear adjustment devices 36 are known to the person skilled in the art and will not be explained in more detail here.
  • the wear adjustment device 36 is adjusted in such a way that the clearance between the friction brake linings 14, 24 and the brake disc 12 increases with increasing wear of the friction brake linings 14, 24 when the disc brake 10 is not actuated.

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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 (10) notamment électromécanique comprenant une garniture de frein à frottement (14) qui peut se déplacer parallèlement à un disque de frein (12) et prend appui contre un élément d'appui (16) qui forme un angle α avec le disque de frein (12). Selon l'invention, l'angle α est choisi dans une première zone (I) de sorte que la relation α = arctan ?max s'applique, et l'angle α est ensuite réduit dans une seconde zone (II) qui succède à la première, de façon continue de sorte que, pour des valeurs de frottement qui décroissent jusqu'à ?min, la relation α = arctan ? s'applique lorsqu'une force de frottement maximale F<SB>R</SB> est atteinte.
PCT/DE2003/000989 2002-06-12 2003-03-26 Frein, notamment frein a disque a amplification automatique et angle d'attaque variable WO2003106857A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002126035 DE10226035A1 (de) 2002-06-12 2002-06-12 Bremse, insbesondere Scheibenbremse
DE10226035.4 2002-06-12

Publications (1)

Publication Number Publication Date
WO2003106857A1 true WO2003106857A1 (fr) 2003-12-24

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WO (1) WO2003106857A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005061920A1 (fr) * 2003-12-24 2005-07-07 Robert Bosch Gmbh Frein a friction electromecanique a auto-amplification
WO2007045428A1 (fr) * 2005-10-18 2007-04-26 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein a disque comportant un actionneur a moteur electrique et un dispositif de liberation d'urgence
US8136639B2 (en) 2006-01-26 2012-03-20 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Self-energizing disk brake

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DE102004029841A1 (de) * 2004-06-19 2006-01-05 Robert Bosch Gmbh Selbstverstärkende elektromechanische Reibungsbremse
CN100561004C (zh) * 2004-10-13 2009-11-18 克诺尔商用车制动系统有限公司 按自行增力的结构形式的盘式制动器
DE102005030620A1 (de) 2004-10-13 2006-04-20 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse in selbstverstärkerder Bauart
DE102005027916B4 (de) * 2005-06-16 2013-04-11 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Fahrzeugbremse in selbstverstärkender Bauart
DE102005035608A1 (de) * 2005-07-29 2007-02-08 Robert Bosch Gmbh Selbstverstärkende elektromechanische Scheibenbremse
DE102011119791A1 (de) 2011-11-30 2013-06-06 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Pneumatisch betätigbare Scheibenbremse

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DE1078886B (de) * 1955-08-20 1960-03-31 Teves Kg Alfred Selbstverstaerkende Scheibenbremse, insbesondere fuer Kraftfahrzeuge
US3662864A (en) * 1969-11-05 1972-05-16 Kelsey Hayes Co Disk type brake with split primary shoe
JPS596439A (ja) * 1982-06-29 1984-01-13 Hino Motors Ltd ウエツジブレ−キ
US6305506B1 (en) * 1996-10-03 2001-10-23 Toyota Jidosha Kabushiki Kaisha Braking system including motor-driven disc brake equipped with self-servo mechanism
US6318513B1 (en) * 1998-04-30 2001-11-20 Deutsches Zentrum Fur Luft- Und Raumfahrt E.V. Electromechanical brake with self-energization
DE10046177A1 (de) 2000-09-19 2002-04-04 Bosch Gmbh Robert Scheibenbremse
WO2002095255A1 (fr) * 2001-05-21 2002-11-28 Estop Gmbh Frein electromecanique avec amplification automatique et angle d'attaque variable

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DE1078886B (de) * 1955-08-20 1960-03-31 Teves Kg Alfred Selbstverstaerkende Scheibenbremse, insbesondere fuer Kraftfahrzeuge
US3662864A (en) * 1969-11-05 1972-05-16 Kelsey Hayes Co Disk type brake with split primary shoe
JPS596439A (ja) * 1982-06-29 1984-01-13 Hino Motors Ltd ウエツジブレ−キ
US6305506B1 (en) * 1996-10-03 2001-10-23 Toyota Jidosha Kabushiki Kaisha Braking system including motor-driven disc brake equipped with self-servo mechanism
US6318513B1 (en) * 1998-04-30 2001-11-20 Deutsches Zentrum Fur Luft- Und Raumfahrt E.V. Electromechanical brake with self-energization
DE10046177A1 (de) 2000-09-19 2002-04-04 Bosch Gmbh Robert Scheibenbremse
WO2002095255A1 (fr) * 2001-05-21 2002-11-28 Estop Gmbh Frein electromecanique avec amplification automatique et angle d'attaque variable

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005061920A1 (fr) * 2003-12-24 2005-07-07 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
WO2007045428A1 (fr) * 2005-10-18 2007-04-26 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein a disque comportant un actionneur a moteur electrique et un dispositif de liberation d'urgence
US8136639B2 (en) 2006-01-26 2012-03-20 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Self-energizing disk brake

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