WO2013149777A1 - Étrier de frein à actionnement combiné - Google Patents

Étrier de frein à actionnement combiné Download PDF

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Publication number
WO2013149777A1
WO2013149777A1 PCT/EP2013/054368 EP2013054368W WO2013149777A1 WO 2013149777 A1 WO2013149777 A1 WO 2013149777A1 EP 2013054368 W EP2013054368 W EP 2013054368W WO 2013149777 A1 WO2013149777 A1 WO 2013149777A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
brake caliper
combined
cam
piston bore
Prior art date
Application number
PCT/EP2013/054368
Other languages
German (de)
English (en)
Inventor
Klaus Barabasch
Sebastian Salzmann
Ralph Petri
Götz Mehner
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
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2013149777A1 publication Critical patent/WO2013149777A1/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
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
    • 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
    • F16D2121/14—Mechanical
    • 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
    • F16D2125/20—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
    • F16D2125/36—Helical cams, Ball-rotating ramps

Definitions

  • the invention relates to a combined actuated brake ⁇ saddle comprising a housing having a bore in which a piston is guided axially displaceably guided as ⁇ actuator.
  • the piston is usually hydraulically actuated by means of pressure medium for service braking and for parking braking by a rotationally driven shaft. It is pos ⁇ lich that both service braking and parking brake operations are performed by electromechanical actuators. Gear means and anti-rotation means serve to convert a rotary drive rotary motion into a translational output motion from the actuator.
  • EP 403 635 B1 describes a combined actuated brake caliper of a motor vehicle disc brake.
  • the known caliper comprises a housing, wherein a piston is arranged axially ver ⁇ slidably guided in a piston bore, and is acted upon by transmission means with at least one ball ramp device.
  • the ball ramp device comprises a rotatable and axially displaceably mounted in the housing drive transmission component with an actuating shaft and a ball ramp assembly, which is supported on a non-rotatably and axially immovably mounted in the housing counterpart.
  • To form a bundled preassembly assembly (insert) a common fastening element is additionally provided, so that the assembly formed as a whole can be inserted into the piston bore.
  • An essential component of this assembly is the counterpart of the ball ⁇ ramp assembly formed as a perforated plate, and secured against rotation in relation to the housing, at a bottom of Housing is added. As a result, the entire pre-assembly ⁇ is taken against rotation in the housing, and peripheral forces are introduced from the assembly on the plate in the ground.
  • the object is achieved by the combination of the features of the main claim by at least one in the housing against rotation and axially displaceable mounted output ⁇ transmission component and a rotatable relative to the housing and axially non-displaceably mounted drive transmission component is provided, and wherein the housing, to form the
  • At least one circular segment-shaped Ausneh ⁇ tion has, which is arranged parallel to the piston bore prismatic, and at least one radially outwardly facing cam directly or indirectly from the non-rotatably mounted output gear component formschlüs ⁇ sig in the Recess engages.
  • a particular advantage of the invention is the surprising effect that the transmission means despite Eliminie ⁇ tion of an additional component (cartridge, Befest Trentsele ⁇ ment) have increased resistance to overloading. With improved power flow increased radio ⁇ tion security is created. Inner wear is avoided the. In a particularly favorable production of the subassembly, the fatigue strength is increased according to the invention.
  • FIG. 2a shows the detail IIa in Fig. 1 in plan view along the axis A, partially cut and enlarged
  • FIG. 3 shows the arrangement of FIG. 2b partially in perspective and in section
  • Fig. 4a, b exploded view of transmission components in Fig. 1, each offset by 180 °,
  • Fig. 5 exploded view of transmission components according to a second embodiment with odd number of cams
  • Fig. 6 shows the embodiment as in Fig. 5 in 180 ° rotated exploded view.
  • a caliper 1 of Faustseltype used to generate application forces has a housing 2, which has a leg 3, a bridge section 4 and so-called fist ⁇ finger 5.
  • the housing consists Since ⁇ at engages over the bridge portion 4 a brake disc 6.
  • the actuator 7 - in particular piston - is axially displaceable in an axially directed, and at least partly stepped manufactured arranged piston bore 8 and actuates a brake pad directly.
  • the brake lining is pressed against a friction surface of the brake disc.
  • the brake pads are arranged on both sides of the brake disc.
  • a vehicle-mounted holder receives the brake pads so that tangentially directed brake circumferential forces can be introduced into the vehicle.
  • the housing 2 is arranged with its leg 3 axially displaceably guided on the vehicle-fixed holder to act by reaction force indirectly actuated brake pad against the friction surface of the brake disc 6, and thereby apply the clamping forces.
  • Gear means comprise at least one axially on the housing 2 fixed and rotatably mounted relative to the housing 2 on ⁇ transmission gearbox 9.
  • This rotationally driven GE drive component has a drive shaft 10 and a synchronous xwindbare ball ramp device 11.
  • the transmission means further have an associated and non-rotatably mounted on the housing 2, and translationally displaceable, output gear member 12 with a ball ramp device 13, which the actuating element 7 (piston ) actuated indirectly by means of a so-called Ver ⁇ wear-adjusting device.
  • the driven gear component 12 has a threaded spindle 15, which meshes with a threaded nut 16, which is axially elastically biased by a friction cone 17 to form a coupling on a conical counterpart of the actuating element 7 (piston).
  • the output gear member 12 is at least one
  • Output gear component 12 rotatably coupled to the housing 2.
  • the anti-rotation device 18 is equipped with an integrated guide function, the
  • the axially displaceable and non-rotatably received output gear component 12 has an adapted, radially outwardly facing, cam 20.
  • the cam 20 engages positively in the circular segment-shaped recess 19. Between the surface of the recess 19 and the cam 20 is in the radial direction at least selective contact. This gives the
  • Anti-rotation function additionally a supporting guide tion function for the translatory displacement.
  • Output gear component 12 is integrally formed with the threaded spindle 15, and with one or more cams 20, and with a plurality of ball ramp contours.
  • a irr ⁇ moderate number of several anti-rotation devices 18, 18 ', 18''is particularly suited for housing 2, which are made of an aluminum material ⁇ . Because compressive stresses are ⁇ initiated advantageous distributed in the housing 2.
  • the geometry data from the circle segment are advantageously chosen in this context so that the circle segment has ei ⁇ nen smaller radius r, as the radius R of Kol ⁇ benbohrung.
  • a circle center M of the circle segment is in the radial direction Ra between
  • the area of the circular segment is always dimensioned substantially smaller than the area of the piston bore.
  • the radius RB is provided stepped such that it is smaller than the radius R of the piston bore.
  • the angular positioning of the circular segment-shaped recess 19,19 ' is advantageously arranged in the range of a mechanically very stiff dimensioned bridge section 4 of the housing 2.
  • This positioning is also referred to as the 12 o'clock position in the broader context.
  • Radially diametrically opposite the bridge section is a so-called 6 o'clock position, which advantageously also has a guide with a circular segment.
  • the 6 o'clock position is diejeni ⁇ ge position on the circumference of the piston bore, which, viewed in radial direction has the smallest distance to a rotation axis Ax of the brake disc.
  • anti-rotation devices 18, 18 ', 18'' For a further uniform distribution of forces, it is possible in principle to increase the number of anti-rotation devices 18, 18 ', 18''. Particularly preferred is an odd number of anti-rotation 18, 18 ', 18''on the circumference of the piston bore 8 is provided. All anti-rotation locks 18 are each arranged at a regular distance from one another at the circumference of the piston bore 8 at a regular angle. Two or more anti-rotation 18, 18 ', 18''allow a particularly favorable force for certain material pairings, for example, if the output gear member 12 is formed of fes ⁇ tem material such as steel, so that the cams in a housing 2 made of ductile material, such as ⁇ example in aluminum material, is included.
  • each cam 20 has at least one ge ⁇ curved portion 21, which is nestled arc to the arc contour of the receiving segment of a circle in order to avoid deformation or clamping.
  • each curved portion 21 of a cam to a radius rl, which largely coincides with the radius r of the circle segment.
  • this clearance 22 is also formed circular segment-shaped, in that the head of the cam 20 is flattened thus formed flat.
  • the space 22 thus allows a certain amount of space in the radial direction, so that too narrow tolerance can be avoided.
  • a further advantageous measure to improve the carrying capacity ⁇ is that several anti-rotation devices 18, 18 ', 18''with play are tolerated each other. As a result, a particularly uniform load distribution between the individual anti-rotation locks 18, 18 ', 18''is achieved.
  • the assembly of the components in the piston bore 8 is as follows.
  • a radially effective bearing bush 23 is inserted into a circumferential area of a through-bore 24 from the bottom 25.
  • the bushing 23 receives the drive shaft 10 from Antriebsge ⁇ drive component 9 rotatably.
  • a thrust bearing 26 is introduced to the housing side, axially directed support of the drive gear member 9 through the piston bore 8 through, and placed on the bottom 25 of the piston bore 8 ⁇ .
  • the rotatable drive gear member 9 is inserted with its shaft 10 in the through hole 24.
  • the actuating element 7 forms a preassembly assembly, which comprises the actuating element 7, a threaded nut 16, a thrust bearing 27 and at least one spring element 28 which is provided between a projection of the Betätigunselement 7 and the thrust bearing 27 elastically clamped.
  • the pre-assembly is inserted into the housing, and the Ge ⁇ windemutter 16 is screwed onto the output gear component 15 ⁇ .
  • a pre-installed on the actuator 7 (Kol ⁇ ben), ie preassembled and separately hand ⁇ habitable assembly with the output gear component 12 is inserted into the piston bore 8. So the involved construction ⁇ groups ranging from the friction cone 17 split are provided.
  • the integrated sub-assembly in the actuating element (piston) 7 is provided with the aid of a spring element 30 elastically biased in the axial ⁇ direction Ax on the ball ramp device 11 from the drive gear component 9.
  • the Fe ⁇ derelement 30 between a head of Output gear component 12 and the spring cup 29 is clamped ⁇ .
  • the spring cup 29 is supported directly or indirectly on the housing 2.
  • the support is preferably carried out with ⁇ telbar by means of a separate fastening element (clamping ring) 31, which engages positively in a recess on the Ge ⁇ housing. 2

Landscapes

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

Abstract

L'invention concerne un étrier de frein (1) à actionnement combiné d'un frein à disque d'un véhicule automobile, comprenant un carter (2), un piston (1) étant guidé de manière mobile par coulissement dans un alésage de piston (8) et soumis à l'action d'engrenages qui comportant au moins un dispositif de rampe à billes (11, 13), lequel dispositif de rampe à billes comprend au moins un élément d'engrenage mené (12) logé de manière bloque en rotation dans le carter ainsi qu'un élément d'engrenage menant (9) pouvant tourner par rapport à l'élément d'engrenage mené, pour permettre un actionnement du frein de stationnement au moyen d'un mouvement rotatif d'entraînement. Le carter (2) comporte, sur la circonférence de l'alésage de piston (8), pour créer une protection (18) contre la rotation, au moins un évidement (19) en segment de cercle orienté radialement vers l'extérieur en partant de la circonférence, lequel est agencé parallèlement en prisme par rapport à l'alésage de piston (8), formant ainsi un évidement (19) servant à loger par guidage axial au moins une came (20).
PCT/EP2013/054368 2012-04-04 2013-03-05 Étrier de frein à actionnement combiné WO2013149777A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102012205548.7 2012-04-04
DE102012205548 2012-04-04
DE102012223138A DE102012223138A1 (de) 2012-04-04 2012-12-13 Kombiniert betätigbarer Bremssattel
DE102012223138.2 2012-12-13

Publications (1)

Publication Number Publication Date
WO2013149777A1 true WO2013149777A1 (fr) 2013-10-10

Family

ID=49210005

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/054368 WO2013149777A1 (fr) 2012-04-04 2013-03-05 Étrier de frein à actionnement combiné

Country Status (2)

Country Link
DE (1) DE102012223138A1 (fr)
WO (1) WO2013149777A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104712689A (zh) * 2015-03-02 2015-06-17 武汉万向汽车制动器有限公司 带驻车机构的盘式制动缸总成及制动钳
US20210300310A1 (en) * 2020-03-31 2021-09-30 ZF Active Safety US Inc. Electromechanical brake apparatus and system with adjustment features
CN114658778A (zh) * 2022-03-31 2022-06-24 长沙泊呈科技有限公司 制动用驱动缸及具有该制动用驱动缸的盘式制动装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3072348B1 (fr) * 2017-10-18 2019-11-08 Robert Bosch Gmbh Module hydraulique de servofrein electrohydraulique integre

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0403635B1 (fr) 1989-01-11 1992-08-26 Lucas Industries Public Limited Company Dispositif d'actionnement a reglage automatique pour freins de vehicules
WO2001018423A1 (fr) * 1999-09-07 2001-03-15 Akebono Corporation North America Actionneur de frein a main autoreglable et logement en materiau leger
EP1757836A1 (fr) * 2005-08-26 2007-02-28 Nissin Kogyo Co., Ltd. Frein à disque
DE102009034503A1 (de) * 2009-06-30 2011-01-05 Continental Teves Ag & Co. Ohg Bremssattel einer Scheibenbremse
US20110155520A1 (en) * 2009-12-25 2011-06-30 Katsuhiro Takahashi Disk brake

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4454933A (en) * 1981-04-27 1984-06-19 Kelsey Hayes Company Disc brake
IT1237110B (it) * 1988-10-24 1993-05-18 Kelsey Hayes Co Freno di stazionamento meccanico integrale con un freno a disco automobilistico azionato idraulicamente.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0403635B1 (fr) 1989-01-11 1992-08-26 Lucas Industries Public Limited Company Dispositif d'actionnement a reglage automatique pour freins de vehicules
WO2001018423A1 (fr) * 1999-09-07 2001-03-15 Akebono Corporation North America Actionneur de frein a main autoreglable et logement en materiau leger
EP1757836A1 (fr) * 2005-08-26 2007-02-28 Nissin Kogyo Co., Ltd. Frein à disque
DE102009034503A1 (de) * 2009-06-30 2011-01-05 Continental Teves Ag & Co. Ohg Bremssattel einer Scheibenbremse
US20110155520A1 (en) * 2009-12-25 2011-06-30 Katsuhiro Takahashi Disk brake

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104712689A (zh) * 2015-03-02 2015-06-17 武汉万向汽车制动器有限公司 带驻车机构的盘式制动缸总成及制动钳
US20210300310A1 (en) * 2020-03-31 2021-09-30 ZF Active Safety US Inc. Electromechanical brake apparatus and system with adjustment features
US11511715B2 (en) * 2020-03-31 2022-11-29 ZF Active Safety US Inc. Electromechanical brake apparatus and system with adjustment features
CN114658778A (zh) * 2022-03-31 2022-06-24 长沙泊呈科技有限公司 制动用驱动缸及具有该制动用驱动缸的盘式制动装置

Also Published As

Publication number Publication date
DE102012223138A1 (de) 2013-10-10

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