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WO1999027271A1 - Frein a disque a actionnement electromecanique - Google Patents

Frein a disque a actionnement electromecanique Download PDF

Info

Publication number
WO1999027271A1
WO1999027271A1 PCT/EP1998/007473 EP9807473W WO9927271A1 WO 1999027271 A1 WO1999027271 A1 WO 1999027271A1 EP 9807473 W EP9807473 W EP 9807473W WO 9927271 A1 WO9927271 A1 WO 9927271A1
Authority
WO
WIPO (PCT)
Prior art keywords
disc brake
force
threaded spindle
disc
threaded
Prior art date
Application number
PCT/EP1998/007473
Other languages
German (de)
English (en)
Inventor
Ralf Schwarz
Original Assignee
Continental Teves Ag & Co. Ohg
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
Priority claimed from DE19757038A external-priority patent/DE19757038A1/de
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO1999027271A1 publication Critical patent/WO1999027271A1/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
    • 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
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/003—Position, angle or speed
    • 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
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • 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
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement
    • F16D2125/50—Rotating members in mutual engagement with parallel non-stationary axes, e.g. planetary gearing

Definitions

  • the invention relates to a disc brake for motor vehicles which can be actuated by means of an electric motor with the interposition of an axially adjustable threaded spindle having a reduction gear, with a brake caliper, with two friction linings interacting with one side surface of a brake disk and arranged to be displaceable to a limited extent in the brake caliper, one of the friction linings being directly and through the threaded spindle the other friction lining can be brought into engagement with the brake disc by the action of a reaction force applied by the brake caliper.
  • Such an electromechanically actuated disc brake is known for example from DE 195 11 287 AI.
  • the actuating unit of the known disc brake consists of an electric motor, an actuating element and a reduction gear arranged between the electric motor and actuating element, which is designed as a roller screw drive with return of the thread rollers.
  • the friction lining assigned to the actuating unit is brought into engagement with the brake disc by an axial displacement of the spindle of the roller screw drive.
  • the actuating element is formed by the spindle of the roller screw drive, the threaded nut of which is driven by the electric motor in order to generate a corresponding clamping force.
  • the storage of the threaded nut serves a large diameter crossed roller bearing arranged in the brake caliper.
  • a disadvantage of the known electromechanically actuated disc brake is the considerable load on the spindle caused by transverse forces, which occur particularly in the case of large travels (worn brake pads) and are due to the effect of circumferential forces on the pads and the expansion of the brake caliper that occurs when the actuating unit is actuated.
  • the cross roller bearing is ovalized by the expansion of the brake caliper, which causes a deterioration in efficiency due to increased bearing friction torque.
  • the guide in the direction of action of the threaded spin del applied force (clamping force) is flexible and rigid in the circumferential direction.
  • a particularly advantageous development of the subject of the invention is characterized in that the guide is formed by a cylinder guided in a bore in the brake caliper and by a plate carried by the cylinder, with the central area of which the spindle is in a force-transmitting connection.
  • the guide is formed by at least two axially adjustable guide bolts and a plate carried by the bolts, with the central area of the threaded spindle being in a force-transmitting connection.
  • a further advantageous embodiment of the invention provides that the central area of the plate is flexible in the effective direction of the force (clamping force) applied by the threaded spindle and rigid in the circumferential direction, in particular is made of spring steel.
  • a significant improvement in the efficiency of the disc brake according to the invention is finally achieved in a further advantageous embodiment of the invention in that the power transmission between the rotor of the electric motor and the threaded nut of the reduction gear takes place by means of a planetary gear which acts on the end of the threaded nut facing away from the friction linings.
  • Fig. 1 shows a first embodiment of the electromechanically actuated disc brake according to the invention in axial section
  • Fig. 2 shows a detail of a second embodiment of the disc brake according to the invention in axial section.
  • the electromechanically actuated disc brake according to the invention shown in FIG. 1 of the drawing which in the example shown is designed as a floating caliper disc brake, essentially consists of a brake caliper 1 which is displaceably mounted in a fixed holder (not shown) and an actuating unit 2, the housing of which 8 is arranged on the brake caliper 1 by means of fastening elements, not shown.
  • a pair of friction pads 4 and 5 is arranged in the brake caliper 1 such that they face the right and left side surfaces of a brake disc 3.
  • the friction lining 4 shown on the right in the drawing is referred to below as the first friction lining and the other friction lining, designated 5, as the second friction lining.
  • Actuating element 30 can be brought directly into engagement with the brake disk 3 by the actuating unit 2, the second friction lining 5 is pressed against the opposite side surface of the brake disk 3 by the action of a reaction force applied by the brake caliper 1 when the arrangement is actuated.
  • the above-mentioned actuation unit 2 consists of an electric motor 6, which in the example shown is designed as a permanent magnet excited, electronically commutatable (torque) motor, the stator 9 of which is immobile is arranged in the housing 8 and its rotor 10 or hollow shaft is formed by an annular carrier 15 which carries a plurality of permanent magnet segments 16. Between the torque motor 6 and the actuating element 30, which was mentioned above and is preferably arranged coaxially to the motor 6, a reduction gear 7 is arranged, which in the example shown is designed as a roller screw drive 11 to 14.
  • the roller screw drive consists essentially of a threaded nut 11 and a threaded spindle 14, with threaded rollers 12, 13 being arranged axially parallel between the threaded nut 11 and threaded spindle 14, which rotate in a planetary manner when the threaded nut 11 rotates and set the threaded spindle 14 in a translational movement.
  • the arrangement is preferably such that the threaded nut 11 is driven by the rotor 10 of the torque motor 6 by means of a planetary gear 17, 18, 19, 20, 21.
  • the planetary gear consists of a sun gear, which is formed by a toothed region 17 formed at the end of the rotor 10, a plurality of planet gears, one of which is shown and provided with the reference number 18, a ring gear 19, which is formed by an internal toothing 20 formed in the housing 8 is formed, and a planet carrier 21, which is preferably attached to the end of the threaded nut 11.
  • the planet gear carrier 21 is supported in the housing 8 of the actuating unit 2 by means of a radial bearing 22.
  • the threaded nut 11 is mounted in a bearing 23 which absorbs axial and radial forces and is provided in a bearing holder 29 arranged in the brake caliper 1.
  • the backlash can be reduced to improve the resilience reconstruction and control quality.
  • the previously mentioned bearing holder 29 can preferably accommodate a clamping force sensor system, not shown, since the entire clamping forces are supported via it.
  • the aforementioned actuating element 30 is formed by the threaded spindle 14, the end of which faces the first friction lining 4 cooperates with a linear guide which is provided with the reference symbol 24.
  • the guide 24 is formed by a cylinder 26 which is axially adjustable in a bore 25 in the brake caliper 1 and which carries at its end facing the first friction lining 4 a metallic plate 27 of small material thickness, over the central area of which the power transmission from the threaded spindle 14 takes place on the first friction lining 4.
  • the plate 27, which is preferably made of spring steel, is flexible in the direction of force transmission, but is rigid in the transverse direction.
  • a force transmission part or a pressure mushroom 28 is provided, which is connected to the threaded spindle 14, for example by means of a threaded bolt.
  • the described configuration of the linear guide 24 or 26, 27 ensures that the pressure mushroom 28, which is axially in contact with the first friction lining 4, is on the one hand due to the movement of the cylinder 26 in the bore 25 and on the other hand also by bending the plate 27 in the axial direction can move, the transverse forces acting on the pressure mushroom 28 are derived via the cylinder 26 directly into the brake caliper 1.
  • a contactless sensor or angle sensor is provided in the housing 8 of the actuating unit 2.
  • a so-called resolver 31 is used as the measuring or angle transmitter, which consists of two rings 32, 33 which are coaxially separated from one another by an air gap and which carry electrical windings.
  • the radially inner ring 32 is connected to the threaded nut 11, while the other, radially outer ring 33 is arranged in a rotationally fixed manner in the housing 8.
  • another embodiment, not shown, is also conceivable, in which for the
  • a radial bearing is arranged, which is used to support the threaded nut or the planet carrier connected to it.
  • the housing 8 is provided with large-area cooling fins 40.
  • the aforementioned linear guidance of the threaded spindle 14 is formed by guide bolts 36, 37 axially adjustably guided in the brake caliper 1 in two bores 34, 35 formed parallel to one another and a force transmission plate which bears the reference number 38 .
  • the force transmission plate 38 is fastened to the ends of the guide bolts 36, 37 facing the first friction lining 4 and has a central region 39 formed by a thin plate, which, as already mentioned in connection with the embodiment shown in FIG Guide bolts 36, 37 enable a force transmission between the threaded spindle 14 and the friction lining 4 by its bending in the axial direction.

Landscapes

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

Abstract

L'invention concerne un frein à disque pour véhicules automobiles, pouvant être actionné au moyen d'un moteur électrique avec intercalation d'un engrenage réducteur, qui comporte un étrier flottant dans lequel sont disposées, de façon à pouvoir se déplacer, deux garnitures de friction. L'engrenage réducteur se présente sous la forme d'un engrenage à rouleaux filetés avec asservissement desdits rouleaux filetés, dont la broche se déplaçant axialement met en contact une des deux garnitures de friction avec un disque de frein. Afin, en particulier, que l'influence de forces et de couples perturbateurs soit minimisée, il est proposé, selon l'invention, que la broche filetée (14) coopère, à son extrémité faisant face à la première garniture de friction (4), avec un guide linéaire (24) qui peut fléchir dans le sens effectif de la force (force de serrage) exercée par la broche filetée (14) et qui ne peut pas fléchir dans le sens périphérique.
PCT/EP1998/007473 1997-11-21 1998-11-20 Frein a disque a actionnement electromecanique WO1999027271A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19751616.5 1997-11-21
DE19751616 1997-11-21
DE19757038A DE19757038A1 (de) 1997-11-21 1997-12-20 Elektromechanische Bremse
DE19757038.0 1997-12-20

Publications (1)

Publication Number Publication Date
WO1999027271A1 true WO1999027271A1 (fr) 1999-06-03

Family

ID=26041793

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/007473 WO1999027271A1 (fr) 1997-11-21 1998-11-20 Frein a disque a actionnement electromecanique

Country Status (1)

Country Link
WO (1) WO1999027271A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112392875A (zh) * 2019-08-13 2021-02-23 英国美瑞特重型车制动系统有限公司 盘式制动器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4356897A (en) * 1978-12-29 1982-11-02 Eaton Corporation Wear indicator for disc brakes
US5107967A (en) * 1989-07-06 1992-04-28 Honda Giken Kogyo Kabushiki Kaisha Motor disc brake system
US5551536A (en) * 1990-12-10 1996-09-03 Brake And Clutch Industries Australia Pty. Ltd. Pad support for disc brake assembly
DE19508253A1 (de) * 1995-03-08 1996-09-12 Continental Ag Duo-Bremsaktor
JPH08296674A (ja) * 1995-04-26 1996-11-12 Akebono Brake Res & Dev Center Ltd ブレーキ装置
DE19611910A1 (de) * 1996-03-26 1997-10-02 Bosch Gmbh Robert Elektromechanische Bremsvorrichtung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4356897A (en) * 1978-12-29 1982-11-02 Eaton Corporation Wear indicator for disc brakes
US5107967A (en) * 1989-07-06 1992-04-28 Honda Giken Kogyo Kabushiki Kaisha Motor disc brake system
US5551536A (en) * 1990-12-10 1996-09-03 Brake And Clutch Industries Australia Pty. Ltd. Pad support for disc brake assembly
DE19508253A1 (de) * 1995-03-08 1996-09-12 Continental Ag Duo-Bremsaktor
JPH08296674A (ja) * 1995-04-26 1996-11-12 Akebono Brake Res & Dev Center Ltd ブレーキ装置
DE19611910A1 (de) * 1996-03-26 1997-10-02 Bosch Gmbh Robert Elektromechanische Bremsvorrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 097, no. 003 31 March 1997 (1997-03-31) *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112392875A (zh) * 2019-08-13 2021-02-23 英国美瑞特重型车制动系统有限公司 盘式制动器
CN112392875B (zh) * 2019-08-13 2022-06-07 英国美瑞特重型车制动系统有限公司 盘式制动器
US12078216B2 (en) 2019-08-13 2024-09-03 Meritor Heavy Vehicle Braking Systems (Uk) Limited Disc brake

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