WO2006103145A1 - Frein a disque electromecanique a auto-amplification de freinage - Google Patents

Frein a disque electromecanique a auto-amplification de freinage Download PDF

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Publication number
WO2006103145A1
WO2006103145A1 PCT/EP2006/060160 EP2006060160W WO2006103145A1 WO 2006103145 A1 WO2006103145 A1 WO 2006103145A1 EP 2006060160 W EP2006060160 W EP 2006060160W WO 2006103145 A1 WO2006103145 A1 WO 2006103145A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
disc
friction
friction brake
self
Prior art date
Application number
PCT/EP2006/060160
Other languages
German (de)
English (en)
Inventor
Dietmar Baumann
Dirk Hofmann
Herbert Vollert
Willi Nagel
Andreas Henke
Bertram Foitzik
Bernd Goetzelmann
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 WO2006103145A1 publication Critical patent/WO2006103145A1/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
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. 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
    • 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
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0062—Partly lined, i.e. braking surface extending over only a part of the 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
    • 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
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/08—Self-amplifying or de-amplifying mechanisms
    • F16D2127/10—Self-amplifying or de-amplifying mechanisms having wedging elements
    • 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
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces

Definitions

  • the invention relates to a self-energizing electromechanical disc brake with the features of the preamble of claim 1.
  • Such a disk brake is known from the published patent application DE 101 49 695 A1.
  • the known disc brake has a floating caliper, d. H. a transverse to a brake disc slidable caliper, in which both sides of the brake disc, two friction brake pads are arranged.
  • an electromechanical actuating device also called an actuator
  • the pressing of a friction brake pad against one side of the brake disc shifts the floating caliper transversely to the brake disc, whereby the other friction brake pad is pressed against the other side of the brake disc and the brake disc is braked.
  • the electromechanical actuator is not explained in detail in the cited publication. It is customary to use an electric motor which uses a rotary / translational gearbox to apply a friction brake lining against the ons / Translations conversion gear presses a friction brake pad against the brake disc. In many cases, a reduction gear is interposed between the electric motor and the rotation / translation conversion gear.
  • the rotation / T ranslations conversion gear for example, be a rotatable or pivotable cam, which acts on the friction brake pad and presses against the brake disc. Usual are helical gears.
  • an electric motor is common, it is not mandatory. It is also conceivable, for example, a linear motor, an electromagnet or a piezoelectric element for pressing the one friction brake lining against the brake disc, so for braking operation.
  • one of the two friction brake linings is displaceable in a circumferential direction, possibly also in a tangential or secant direction to the brake disk.
  • the known disc brake of the friction brake pad is displaceable in the circumferential direction of the brake disc, which is pressed with the actuating device against the brake disc.
  • the other friction brake pad can be displaced.
  • a mechanical self-energizing device converts a frictional force applied to the friction brake pad pressed against it in the circumferential direction during braking from the rotating brake disk into a pressing force which presses the friction brake pad against the brake disk in addition to a pressing force applied by the actuating device and thereby amplifies the braking force.
  • the known disc brake has a wedge mechanism with an extending at an acute angle to the brake disc and in the direction of the friction brake pad wedge surface on which the friction brake pad is supported.
  • the friction force exerted on the friction brake lining by the rotating brake disk acts on the friction brake lining in the direction of a wedge gap between the wedge surface and the brake disk, the friction brake lining is pressed into the narrowing wedge gap, the support on the wedge surface due to a wedge effect Pressure force of the friction brake pad against the brake disc causes.
  • the wedge surface is not flat but has a gradient that changes over its course, it may also be spoken a ramp mechanism.
  • a changing self-reinforcement is achieved with the displacement of the friction brake pad, it can be overcome by an initially large slope a clearance between the friction brake pad and the brake disc and towards the end of the shift, ie achieve high self-boost at high braking force .
  • lever mechanisms with inclined to the brake disc the sliding friction brake lining supporting, loaded on train or pressure pivoting levers are known to achieve a self-reinforcing.
  • a support angle between the pivotable lever and a normal to the brake disc corresponds to the wedge angle of a wedge mechanism.
  • Such a lever mechanism is a mechanical equivalent to a wedge mechanism.
  • hydraulic self-reinforcing devices are known per se.
  • All these self-reinforcing devices have in common that one of the two friction brake linings of the disc brake shifts during braking in the circumferential direction (or in the tangent or secant direction) of the brake disc.
  • the two friction brake linings are no longer exactly opposite one another during braking, but have an offset in the circumferential direction of the brake disk.
  • This offset of the friction brake linings pressing against the brake disk causes a moment on the floating caliper about an imaginary radial to the brake disk. This moment must be supported by guides of the floating caliper, which guide the floating caliper transversely to the brake disc.
  • the guides must be correspondingly larger in size and the explained, acting on the floating caliper during braking moment tends to jamming of the floating caliper leads in his guides.
  • the cited publication provides for the friction brake linings to be arranged with an offset in the circumferential direction of the brake disk when the disc brake is not actuated, so that, when the brake is actuated at maximum speed, Shift are congruent.
  • Maximum displacement means worn brake linings and maximum braking force.
  • the friction lining in the circumferential direction of the brake disk causing the self-amplification is shorter in the circumferential direction of the brake disk than the oppositely disposed friction brake lining, at least in a preferred direction of rotation of the brake disk.
  • the friction brake lining which is displaceable in the circumferential direction of the brake disk, is so much shorter in the circumferential direction of the brake disk that it is covered over its entire surface at a maximum displacement from the other, opposite friction brake lining.
  • the preferential direction of rotation of the brake disc is determined by the forward drive of the motor vehicle.
  • Backward braking is much less common and also occurs at low speed and usually low braking power. For this reason, no provision must be made for the direction of rotation of the brake disk in the opposite direction of rotation against the moment that two friction brake linings pressed against the brake disk with an offset in the circumferential direction exert on the brake caliper. Nevertheless, an embodiment of the invention also provides in the preferred direction of rotation of the brake disc opposite direction of rotation before a shorter sliding friction brake lining in the circumferential direction.
  • the invention has the advantage that due to the full-area covering of the displaceable friction brake lining by the opposing friction brake lining during a brake operation, the two friction brake linings pressed against the brake disk do not cause a moment about an imaginary radial to the brake disk on the brake caliper.
  • a transversely displaceable to the brake disc leadership of trained as a floating caliper caliper must therefore not the caliper support against such a moment, the transverse displacement, also called floating movement, the caliper is not complicated.
  • Another advantage of the invention is an improved initiation of the braking force of the friction brake linings pressed against the brake disc into the brake disc and a more uniform surface pressure of the displaceable friction brake pad.
  • FIG. 1 shows a disc brake according to the invention in a view with a view radially from the outside on a brake disc;
  • FIG 3 shows a section of the disc brake of Figure 1 in a radial plane to the brake disc according to line IM -IM.
  • the illustrated in the drawing, inventive, self-energizing electromechanical disc brake 1 has a floating caliper 2 as a caliper.
  • the caliper 2 is a so-called. compassionattel, he has two mutually parallel, flat caliper plates 3, which are rigidly connected with anchors 4 together. Between the two brake caliper plates 3 is a Brake disc 5, to which the two brake caliper plates 3 are parallel.
  • As an anchor 4 find bolts use that are outside a circumference of the brake disc 5.
  • the armature 4 and with them the brake caliper 2 in total are guided transversely to the brake disc 5 in schematically illustrated sliding guides 6. Because of its displaceability transverse to the brake disc 5, the caliper 2 is also referred to as a floating caliper.
  • Reibbremsbeläge 7, 8 are arranged on the brake disc 5 facing inner sides of the brake caliper plates 3 Reibbremsbeläge 7, 8 are arranged.
  • One of the two Reibbremsbeläge 7 is fixed, d. H. immovably arranged on the one caliper plate 3.
  • the other friction brake pad 8 is in the circumferential direction of the brake disc 5, strictly speaking on a helical path at an acute angle to the brake disc 5, displaceable.
  • the Reibbremsbelag 8 on one of the brake disc 5 facing away from trough-shaped depressions, the double ramps 9 form.
  • the double ramps 9 extend in the circumferential direction of the brake disc 5, they are in their longitudinal center at the lowest and flat in both directions, d. H. they rise in both circumferential directions.
  • the caliper plate 3 has on its brake disc 5 and thus the friction brake pad 8 facing front corresponding double ramps 10.
  • the corresponding double ramps 9, 10 balls or rollers are arranged as rolling elements 11.
  • the rolling elements 11 roll on diametrically opposed ramp paths of the double ramps 9, 10 and press the friction brake lining 8 off the brake caliper plate 3 and against the brake disk 5.
  • the caliper 2 designed as a floating caliper becomes transverse shifted to the brake disc 5 and presses the fixed friction brake lining 7 against the other side of the brake disc 5, which is braked.
  • the sliding friction brake lining 8 is always displaced in the direction of rotation of the brake disc 5.
  • the rotating brake disk 5 exerts a frictional force in the direction of rotation on the friction brake lining 8 pressed against it, which additionally supports the friction brake lining 8 in the displacement direction. direction.
  • About the double ramps 9, 10 of the friction brake pad 8 is pressed against the brake disc 5.
  • the double ramps 9, 10 thus convert the frictional force exerted by the rotating brake disk 5 on the friction brake lining 8 pressed against it into a pressing force which presses the friction brake lining 8 against the brake disk in addition to a pressing force exerted by an electromechanical actuating device to be described 5 presses.
  • the disc brake 1 has a self-reinforcing.
  • the shifted in the direction of rotation of the brake disc 5 position of the friction brake pad 8 with actuated disc brake 1 is shown in Figure 1 with dashed lines.
  • the ramps are already formed as double ramps with increase in both circumferential directions of the brake disc 5.
  • the friction brake pad 8 is also displaced in the reverse direction, ie again in the direction of rotation of the brake disc 5 and the disc brake 1 has the self-boosting effect described. If a self-amplification for one direction of rotation of the brake disk 5 is sufficient, then single ramps with an increase only in the direction of rotation of the brake disk 5 are sufficient instead of the illustrated and described double ramps 9, 10.
  • the electromechanical actuating device has an electric motor and a mechanical gear, its direction of action can be between parallel to the brake disc 5 to transverse to the brake disc 5.
  • the actuating device preferably acts parallel to the ramp surfaces of the double ramps 9, 10, ie in the direction of displacement of the friction brake lining 8.
  • the displaceable friction brake lining 8 is shorter in the circumferential direction of the brake disk 5 than the fixed friction brake lining 7, so that the movable friction brake lining 8 is covered even over the entire area by the fixed friction brake lining 7 even with the greatest possible displacement.
  • maximum displacement of the friction brake lining 8 means a maximum braking force of the disc brake 1 and a completely worn friction brake lining 8.
  • the friction brake linings 7, 8 are shown in FIG. 2 without any other parts of the disc brake 1, with dashed lines indicating the maximum displacement of the movable friction brake lining 8 is.
  • the full-surface coverage of the sliding friction brake pad 8 through the fixed friction brake lining 7 has the advantage that no displacement of the friction brake linings 7, 8 in the circumferential direction of the brake disc 5 is formed by the displacement of the friction brake lining 8 in the circumferential direction of the brake caliper 2, due to the pressing forces the friction brake pads 7, 8 would cause against the brake disc 5 by an imaginary radial to the brake disc 5 on the caliper 2.
  • the caliper 2 is torque-free, its sliding guide 6 needs no moment to support.
  • the covering of the displaceable friction brake lining 8 by the fixed friction brake lining 7 when the disc brake 1 is actuated leads to an improved introduction of the braking force from the friction brake linings 7, 8 into the brake disk 5 and to a more uniform surface pressure of the displaceable friction brake lining 8.
  • the displaceable friction brake lining 8 has a greater thickness than the fixed friction brake lining 7, the difference in thickness in the drawing being exaggerated for clarity.
  • the two friction brake linings 7, 8 have the same or at least approximately the same wear volume.
  • the fixed friction brake lining 7 Due to its greater extent in the circumferential direction of the brake disk 5, a mathematical centroid of the fixed Reibbremsbe- lags 7 are located on a smaller radius than the centroid of the sliding friction brake pad 8, if the fixed friction brake lining 7 as well as the sliding friction brake lining 8 would have the shape of a circular arc section.
  • the fixed friction brake lining 7 therefore has a different shape, as can be seen in FIG. 2, so that the center of gravity of the two friction brake linings 7, 8 have the same or at least approximately the same radius.
  • the sliding friction brake lining 8 has the shape of a circular ring section while the fixed friction brake lining has approximately the shape of a circular segment.
  • the fixed friction brake lining 7 has thereby at its peripheral ends more covering material on a larger radius, whereby its center of gravity is located on a larger radius than in a circular ring section with the same extent in the circumferential direction.
  • Reibbremsbeläge 7, 8 are possible and are within the scope of the invention, in spite of greater extension of the fixed Reibbremsbelags 7 in the circumferential direction, the mathematical centroids of both Reibbremsbeläge 7, 8 are on the same or at least approximately at the same radius. Also by the described measure a more uniform surface pressure of the friction brake linings 7, 8 is achieved.
  • both friction brake linings 7, 8 Due to the center of gravity of both friction brake linings 7, 8 at the same or at least approximately the same radius, a moment caused by the contact forces of both friction brake linings 7, 8 against the brake disc 5 is avoided or at least reduced to the brake caliper 2 by an imaginary secant to the brake disc 5. This also relieves the sliding guides 6.
  • the friction surface radii of the two friction brake linings 7, 8 coincide externally and internally with friction surface radii of the brake disk 5.
  • radially outer and radially inner edges of the friction brake linings 7, 8 are congruent with edges of friction surfaces of the brake disk 5. Since the sliding friction brake lining 8 in the circumferential direction of The reason for this is that neither outside nor inside burrs on the Reibbremsbelägen 7, 8 or the brake disc 5 form, which could break off and jam. This is safety-critical and must therefore be avoided, which is done by the same friction surface radii of the friction brake linings 7, 8 and the brake disc 5. In a simplified embodiment, it is conceivable that not all friction surface radii coincide, but, for example, only the outer friction surface radii of both friction brake linings or the friction surface radii of the displaceable friction brake linings 7.
  • the inner friction surface radius of the sliding friction brake pad 8 is smaller than the inner friction surface radius of the fixed friction brake pad 7. This has several reasons. First, the mathematical centroid of the circumferentially shorter, sliding friction brake pad 8 is displaced inwardly, i.e., in the circumferential direction. H. the radii of the center of gravity of the two friction brake linings 7, 8 are approximated as by the other form of the fixed friction brake lining 7 described above. In addition, the area of the sliding friction brake lining 8 which is shorter in the circumferential direction and thus the wear volume is increased.

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

Abstract

L'invention concerne un frein à disque (1) électromécanique à auto-amplification de freinage. Pour l'actionnement du frein, une garniture de friction (8) est déplacée sur le disque de frein (5) dans une direction de rotation d'un disque de frein (5) et dans un angle aigu. L'invention concerne une autre garniture de friction (7) fixe plus longue dans la direction circonférentielle du disque de frein (5) de telle façon que, pour un déplacement maximal de la garniture de friction (8) mobile, garniture de friction (8) mobile est entièrement recouverte par la garniture de friction (7) fixe. Cela permet d'éviter un moment sur un étrier de frein (2) d'un rayon fictif par rapport au disque de frein (5) en raison d'un décalage des deux garnitures de friction (7, 8) dans la direction circonférentielle. Selon l'invention, la garniture de friction (8) mobile est également plus épaisse que la garniture de friction (7) fixe. Les deux garnitures de friction (7, 8) ont ainsi un volume d'usure au moins approximativement identique.
PCT/EP2006/060160 2005-04-01 2006-02-22 Frein a disque electromecanique a auto-amplification de freinage WO2006103145A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005015108.6 2005-04-01
DE200510015108 DE102005015108A1 (de) 2005-04-01 2005-04-01 Selbstverstärkende elektromechanische Scheibenbremse

Publications (1)

Publication Number Publication Date
WO2006103145A1 true WO2006103145A1 (fr) 2006-10-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/060160 WO2006103145A1 (fr) 2005-04-01 2006-02-22 Frein a disque electromecanique a auto-amplification de freinage

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DE (1) DE102005015108A1 (fr)
WO (1) WO2006103145A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007013421A1 (de) * 2007-03-20 2008-09-25 Siemens Ag Bremseinrichtung mit einem Keilmechanismus
CN102084152B (zh) * 2008-07-04 2016-02-03 克诺尔商用车制动系统有限公司 自增力盘式制动器及其制动衬块

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1475501A1 (de) * 1965-11-27 1969-05-22 Teves Gmbh Alfred Mechanisch betaetigte Teilbelagscheibenbremse
DE10149695A1 (de) * 2001-10-09 2003-04-24 Estop Gmbh Elektromechanische Schwimmsattelscheibenbremse mit Selbstverstärkung

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1475501A1 (de) * 1965-11-27 1969-05-22 Teves Gmbh Alfred Mechanisch betaetigte Teilbelagscheibenbremse
DE10149695A1 (de) * 2001-10-09 2003-04-24 Estop Gmbh Elektromechanische Schwimmsattelscheibenbremse mit Selbstverstärkung

Also Published As

Publication number Publication date
DE102005015108A1 (de) 2006-10-05

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