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
  • F16D65/0006—Noise or vibration control
• • 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
  • F16D2121/02—Fluid pressure
  • F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid 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
  • F16D2125/00—Components of actuators
  • F16D2125/02—Fluid-pressure mechanisms
  • F16D2125/04—Cylinders
• • 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
  • F16D2125/02—Fluid-pressure mechanisms
  • F16D2125/06—Pistons
• • 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
  • F16D2125/02—Fluid-pressure mechanisms
  • F16D2125/08—Seals, e.g. piston seals
• • 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
  • F16D2127/02—Release mechanisms

Definitions

• the invention relates to a guide system for a brake piston of a motor vehicle disc brake comprising a brake piston, a cylindrical brake piston bore for axially relatively displaceable receiving the brake piston in a housing, and a guide means which is elastically clamped between a cylindrical brake piston wall and a groove in the brake piston bore.
• a fixed caliper brake with brake piston-cylinder unit and with a wobble joint for the brake piston known.
• the brake piston receives an elastic seal.
• the brake piston is received by the seal centric in a piston bore and bendable and slidably mounted.
• a brake piston axis can align under pressure in braking orthogonal to a back of a brake pad. The orientation is inevitably dependent on an elastic housing deformation under a growing brake pressure.
• the brake piston is radially symmetrically clamped by the seal (symmetrical clamping).
• NVH Noise Vibration Harshness
• the brake piston guide is the first time “bought and verstimmbares” as modalakustisch relevant and special form understood subsystem of a motor vehicle brake ⁇ system. Due to the special combination of the boundary conditions between the brake piston bore and Bremskolbenwandung the guide means is such reversible elastic "tune” clamped to the guide means to the caliper housing is supported, and the brake piston permanently acted upon with a de ⁇ defined transverse force effect, so that the brake ⁇ piston wall metered with the bore wall as needed, that is controlled, modalacoustic coupled.
• a modalakustisch "eccentric" According to the invention by the novel guide means made upset within the piston receiving Zvi ⁇ rule Bremskolbenwandung and bore so.
• the guide means / ring seal first to have a dual function in such a way that not only the well-known from ⁇ sealing function but administration function a Querkraftmodula- simultaneously
• the system is also standardized and simplified, because its Füh ⁇ approximate function is perceived-primarily through standardized identical parts.
• a brake piston by targeted asymmetric elastic clamping in all operating conditions as needed and low.
• the piston is given a specific orientation, deaxing and / or a defined angle of attack, wherein the brake piston axis can be deaggled even in a pressureless state and / or arranged obliquely to the piston bore.
• piston housing in the housing it is possible with relatively simple means ⁇ light, a piston transversely variable preference ⁇ orientations impose and / or possibly arrange the brake piston axis obliquely in the housing.
• FIG. 2 shows an enlarged view of a part of a brake piston bore according to the invention, including a support for a guide means in a housing, FIG.
• FIGS. 6-7 shows a detail of a mounting situation from the guide means according to FIGS. 6-7 in a housing
• FIG. 11 illustrates details of an installation situation of the guide means according to FIGS. 9 and 10 in a brake piston bore of a housing
• FIG. 12 shows a qualitative comparison to the force effect F of Kolbeneinwear with respect to the piston displacement s using the different configurations, namely according to a) conventional, rigid piston guide system, b) additionally decoupling, centrically biasing guide element, c) eccentrically biasing, eccentric guide element , and d) deaxêt groove between the guide element and / or sealing ring, and Fig. 13 shows a preferred embodiment of the invention, with deaxierter groove and special groove profile, and
• FIG. 14 shows a double-piston application of the embodiment according to FIG. 13.
• the invention can equally both on the guide systems of the brake piston of encoder actuators (ie, for example, hydraulic main ⁇ brake cylinder) or the guide systems for brake piston of slave actuators (ie, for example hydraulic power ⁇ vehicle disc brakes) relate.
• Master brake cylinders usually comprise two hydraulically independently switched, translationally slidably received in a bore, brake piston (primary and secondary pistons), which limit as a sliding wall pressure chambers, which are connected to pressure chambers of associated motor vehicle disc brakes, which in turn are limited by brake piston.
• brake piston primary and secondary pistons
• fixed disc type automotive disc brakes 1 include at least one brake piston 3 on each side of a brake disc 6.
• each volumetrically closed hydraulic system sensors, pipelines, brake hose lines, vehicle disc brake 1,
• Brake piston 3 be ⁇ alsschlagt such fluid pressure according to the law of constant volume inkomp- ressible brake fluid that at least one friction lining 7.8 (directly or indirectly after overcoming a so-called air clearance from the brake ⁇ piston 3 against a brake disk rotor 6) is pressed.
• a surface pressure see brake pressure
• corre ⁇ the encoder is released, unconfirmed.
• the ring seal 9 is received in a recess / groove 10.
• Brake piston 3 is the elasticity and elastic
• a brake piston 3 is basically cup-shaped and comprises a brake piston bottom 11 and a cylindrical
• Brake piston wall 12 Depending on the disc brake type, it may be provided that either the brake piston bottom 11 or a free edge of the brake piston wall 12 directly act on the friction lining 7, 8.
• the guide system 2 for a brake piston 3 an automotive disc brake 1, or other actuators, comprises a concentric and cylindrical arranged for brake piston 3 brake piston bore 13 for axially displaceable recording of the brake piston 3 in the housing 4 (in particular a caliper housing), and mounted in the caliper housing ring seal the elastic between the cylindrical Brake piston 12 and the recess 10 of the brake piston bore 13 is clamped, and serves the functions described above.
• a guide means 15 is provided reversibly elastically clamped in a gap 14 between the brake piston bore 13 and brake piston wall 12, which on
• Brake caliper housing is supported, and the brake piston 3 permanently clamped in the radial direction with a defined force effect such that the brake piston 12 targeted ge ⁇ is coupled to the brake piston bore wall.
• an improved elastically yielding clamping of the guide means 15 results in an improved coupling of transverse forces into the housing 4.
• guide means 15 including ring seal 9 integrally formed, and to arrange in a common recess of the brake piston bore 13.
• guide means 15 and sealing ring 9 may formed as separate components together and be taken up.
• guide means 15 and ring seal 9 are placed at an axial distance from one another in respective separate recesses 10, 16 of the brake piston bore 13.
• the recesses 10,16 may comprise fixing means such as in particular parallel contact ⁇ surfaces 17, 18 for the ring seal 9 and guiding means 15 °. In principle, it makes sense to provide the guide means 15 with a uniform over the brake piston circumference clamping force. As a result, it automatically results in use the brake piston axis A is provided substantially orthogonal to the friction surfaces of the brake disk 6.
• the invention further allows a special, alternative design where between brake piston bore 13 and
• Brake piston 12 a sealed gap 14 extends, and the brake piston axis A is not orthogonal to the friction surface of the brake disc 6 but defined obliquely employed provided.
• This is obtained in one embodiment of the invention by providing a radial force effect of a clamping of the brake piston wall 12 over the brake piston circumference unevenly, and the transverse forces do not neutralize each other.
• the brake piston 3 as a result, a defined transverse force is impressed with a corresponding resulting preferred orientation, wherein the scored ⁇ Anstell ⁇ direction coincides with the direction of force of the resulting transverse force.
• the so unevenly distributed on the brake piston circumference force effect to effect an angle of attack can be obtained by appropriate adaptation of a material elasticity of the guide means 15.
• the brake piston 3 is impressed with a radial transverse force and optionally given a predetermined desired angle of attack.
• the individual ribs 19 or cams extend more long than thick and uniformly extending in the axial direction, that is aligned parallel to the brake piston axis A.
• the height of the ribs 19 defined in this context, in coordination with the outer diameter of the brake piston 12th and the inner diameter of the brake piston bore 13, the radial clamping of the brake piston. 3
• a separate guide means 15 may be formed in a simple variant of Fig. 6-8 as a simple corrugated ring of a solid material (eg spring steel) with a uniform wall thickness, whose cross-section is meandering, and has alternating convex and concave sections. This is a correspondingly adapted coaxial cylindrical brake piston wall and a koaxi ⁇ al-cylindrical brake piston bore 13 assigned.
• the guide means is designed as a bow spring with at least one resilient arm.
• the respective groove receivers for ring seal and / or guide means in the housing deaxiert - ie with axial offset ⁇ with respect to the piston bore - provide.
• the elastic guide means 15 it is possible for the elastic guide means 15 to have at least one component formed at least partially from a metal material, in particular from Fe ⁇ derstahl. It is possible in particular with respect to the azimuth (Az), alternately provide un ⁇ ter Kunststoffliche elasticities / moduli. This is, for example, by the aforementioned Maschinenstoffverbünd and / or other elastomeric More shopping fabric construction made ⁇ light.
• Pressure modulation can be obtained by providing a recess 10,16 for receiving ring seal 9 and or guide means 15 with a profiled base 40 by at least one or more irregularities are provided on the periphery of the base 40.
• the irregularity may be formed as a sectoral flattening, protuberance, recess or other deformation of the base 40 in order to change by appropriately modified recording and action of
• Ring seal 9 and / or guide means 15 according to ver ⁇ changed to obtain modulated spring effects, which circumferentially around the desired and generally radially directed pressure modulation effect on the piston 3.
• the irregularity / s are directed radially in the base surface 40 is preferably provided and may be Favor designed as a radius ⁇ changes, so that the base extends as a non-circular, elliptical, ovoloide or otherwise closed to the brake piston 3 free-form curve.
• the inventive annular guide means 15 is wholly or at least partially made of a plastic material, such as in particular made of PTFE plastic or a PTFE component.
• the guide means 15 is particularly preferably designed annularly, wherein at least one ventilation channel 21 - to a certain extent as a bypass - for the purpose of pressure equalization and for the return flow of pressure medium (brake fluid). liquid) is provided in the pressure chamber 5.
• Each ventilation channel 21 may be configured as a slot 22 provided radially or obliquely on the annular guide means 15. It is possible that the guide means 15 in its wall (in particular radially inward and radially outwardly open) additional channels for better elastic deformation and for the purpose of pressure equalization has. It is possible to form the guide means 15 as a composite of several plastic ⁇ materials in layers and / or with rigid support members to exploit different material properties to optimize the component properties.
• a particular variant of a guide means according to FIGS. 9-11 is that it is designed as a resilient clamp 23 with a plurality of arms extending in a star shape from a center Z.
• the arms 24-27 are accommodated for securing in place in receiving recesses 32-35 from the caliper housing and wherein the free ends 28-31 of the clip 23 each have one or more arms 36,37 have to rest on the circumference of the brake piston 3.
• the arms 36,37 preferably regularly distributed on the circumference intermittently from the outside radially resiliently on the wall of the brake piston 3 and thereby tension the brake piston 3 a.
• FIG. 14 describes by way of example a two-piston application, where K n symbolizes the respective piston. All embodiments provide combinatorial multiple solution features.
• the reference numeral 14 denotes therein in the pairing each a radially measured maximum Game between Bremskolbenwandung 12 and brake piston bore 13 in the housing 4.
• the groove 10 has several, circumferentially offset to each other at an angle of, for example, about ⁇ 60 ° placed, peripheral irregularities (flattening) Ui-U n at your basically annular umlau ⁇ fenden base 40th
• the irregularities U produce in cooperation with the clamped Ring seal 9 and the brake piston 12 an associated radially directed force F] _- F N.
• F radially directed force
• a piston 3 arranged on the left can be acted upon, for example, from the direction of position P3 corresponding to the 8 o'clock position and from the direction of P4 corresponding to the 10 o'clock position.
• the advantageous effect is achieved that the resultant F RK i and F RK 2 neutralize each other.

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

Priority Applications (5)

Applications Claiming Priority (4)

Related Child Applications (1)

Publications (1)

Family

ID=54866267

Family Applications (1)

Country Status (7)

Cited By (2)

Families Citing this family (2)

Citations (4)

Family Cites Families (10)

• 2014
  • 2014-09-24 DE DE102014219334.6A patent/DE102014219334A1/de not_active Withdrawn
• 2015
  • 2015-07-07 KR KR1020167036236A patent/KR102065209B1/ko not_active Expired - Fee Related
  • 2015-07-07 EP EP15735675.9A patent/EP3167202B1/de active Active
  • 2015-07-07 WO PCT/EP2015/065448 patent/WO2016005372A1/de not_active Ceased
  • 2015-07-07 CN CN201590000793.5U patent/CN207064534U/zh not_active Expired - Fee Related
  • 2015-07-07 JP JP2017501035A patent/JP6423949B2/ja not_active Expired - Fee Related
• 2017
  • 2017-01-07 US US15/400,963 patent/US20170114849A1/en not_active Abandoned

Patent Citations (4)

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