WO2009129764A1 - Frein à disque à réglage électrique - Google Patents

Frein à disque à réglage électrique Download PDF

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Publication number
WO2009129764A1
WO2009129764A1 PCT/DE2008/000795 DE2008000795W WO2009129764A1 WO 2009129764 A1 WO2009129764 A1 WO 2009129764A1 DE 2008000795 W DE2008000795 W DE 2008000795W WO 2009129764 A1 WO2009129764 A1 WO 2009129764A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
electrically actuated
disc brake
discs
friction linings
Prior art date
Application number
PCT/DE2008/000795
Other languages
German (de)
English (en)
Inventor
Martin Stadlmeier
Original Assignee
Martin Stadlmeier
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 Martin Stadlmeier filed Critical Martin Stadlmeier
Priority to DE112008003923T priority Critical patent/DE112008003923A5/de
Priority to PCT/DE2008/000795 priority patent/WO2009129764A1/fr
Publication of WO2009129764A1 publication Critical patent/WO2009129764A1/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
    • F16D65/12—Discs; Drums 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
    • F16D55/22—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 clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—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 clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—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 clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—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 clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper 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
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D2065/386—Slack adjusters driven electrically
    • 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
    • F16D2121/20—Electric or magnetic using electromagnets
    • 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
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/24—Rack-and-pinion
    • 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
    • F16D2125/52—Rotating members in mutual engagement with non-parallel stationary axes, e.g. worm or bevel gears
    • 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

Definitions

  • the present invention relates to an electrically controllable disc brake for braking a rotating part with a floating brake caliper, with at least one brake disc whose outwardly directed side surfaces each interact with a friction lining, as well as with an electrical actuating unit for applying a force acting on the friction linings, wherein one of the brake pads is engageable directly by the actuator unit and the other friction pad is engageable with the corresponding surface by the action of a reaction force applied by the caliper.
  • Such a disc brake is z. B. from the European patent application EP 1 384 914 A2.
  • the electric actuation unit is formed in the known disc brake by an electric motor with a downstream transmission, which converts a rotational movement of the electric motor into a translational movement, which is transmitted to an actuating element.
  • actuating element By the actuating element, a clamping force applied by the electric motor is transmitted directly to a friction lining facing the actuating element.
  • a secondary actuator is provided, with which the actuating element is adjustable independently of the actuating unit.
  • WO 02/08039 Al a braking system for motor vehicles is known in which the vehicle front axle is equipped with electromechanically actuated disc brakes of the type mentioned.
  • a disadvantage is the o. G. To see brakes that in the realization of a redundant power supply, which is required for proper operation of such brakes, high-performance energy storage are used, which represent a high cost factor.
  • FIG. 1 shows a first embodiment of variant 1 of the electromechanical disc brake according to the invention in a sectional view
  • FIG. 2 is an illustration of the inner surface of a brake disk used in the embodiment of FIG. 1;
  • FIG. 3 is a section along the section line A - A in Fig. 2,
  • FIG. 4 shows a section along the section line B - B in Fig. 2, 5 shows a second embodiment of variant 1 of the electromechanical disc brake according to the invention in a sectional representation corresponding to FIG. 1;
  • Fig. 6 is an illustration of the inner surface of a brake disc used in the embodiment of FIG. 2;
  • Fig. 7 is a fragmentary view of the second embodiment shown in Figs. 5 and 6;
  • Fig. 9 is a perspective view of details of Fig. 8.
  • FIG. 10 shows a sectional view rotated by 90 ° with respect to FIG. 8 to explain the functional principle of the first embodiment according to FIG. 8;
  • FIG. 13 shows an alternative embodiment of variant 2 for synchronization
  • FIG. 14 is a diagram of a control concept of the present invention.
  • the disk brake according to the invention shown in FIG. 1, which serves to decelerate a provided with the reference numeral 1 rotating part or a shaft has a firmly connected to the shaft 1 ring 2 with at least two gears 3, 4 with trapezoidal cross-section, two on the Shaft 1 arranged brake discs 5, 6 and a floating brake caliper 7, in the friction linings 8, 9 are arranged.
  • the brake discs 5, 6 are mounted rotatably limited on the shaft 1, wherein the limitation by means of cylindrical pins 11, 12 which are received by formed in the shaft 11 guide grooves 13, 14.
  • the brake discs 5, 6 toothed portions 15, 16, with which the aforementioned gears 3, 4 are engaged.
  • the adjusting cylinder 19 is connected via threads to the caliper 7, wherein the dynamics of Lmonspielbergerwindung is dimensioned by the pitch of the threads. Also can be avoided by a self-locking in the absence of supply voltage. For this purpose, the slope is higher than the coefficient of friction of the adjustment.
  • an electromechanical actuator 17 is provided, which is formed in the example shown as an electromagnet whose iron core is formed as a guide pin 18 on which the caliper 7 is mounted.
  • the object of the mentioned actuator 17 is to apply a force acting on the brake caliper 7, which has on the friction linings 8, 9 acting different pressure forces result.
  • the activation of the direction of action of the force applied by the actuator 17 is effected as a function of the direction of travel of the motor vehicle according to the invention equipped with the disc brake. A change in the direction of travel requires the actuator 17 also an opposite control to release the brake or determine.
  • the guide grooves 21 also hold the balls 22 in case of accelerations / vibrations.
  • Fig. 4 shows the principle of operation of the disc brake according to the invention. From a relative rotation of the brake discs 5, 6 to each other, which is indicated by arrows I and II, results in a "spreading apart" of the brake discs 5, 6 or a change in the axial distance between the brake discs, which is due to the interaction of the rising ramp profile of the guide grooves 21 with the balls 22 back.
  • the slope of the ramps is in the range of 0.5 mm.
  • the course can be designed according to an exponential function.
  • the advantage of such an arrangement is that the mechanical translation (gain) in the higher clamping force range is also higher.
  • the force required for the application of the braking force by the actuator 17 is thereby reduced while maintaining the same ramp length.
  • an embodiment of the guide grooves is also conceivable, in which a further ramp in the opposite direction is provided in front of the mentioned region "a ⁇ .
  • a brake application of the disc brake according to the invention in both directions, for example in case of failure of the electrical power supply is possible.
  • the electric motor 20 of the actuating unit 10 is actuated in order to overcome the clearance between the friction linings 8, 9 and the brake discs 5, 6 by means of the adjusting cylinder 19 or to apply the friction linings 8, 9.
  • the electromechanical actuator 17 is actuated, which applies a force acting on the brake caliper 7.
  • the friction lining 8 shown on the left in FIG. 1 is loaded more, while the other friction lining 9 is relieved.
  • the position of the brake discs 5, 6 to each other by the actuator 17 is regulated in the starting position.
  • the brake discs 5, 6 rotate back.
  • the adjustment of the clearance is made by the rotation angle (time) of the return travel.
  • the adjustment of the brake pads 8, 9 automatically adjusts itself with each actuation and backward movement of the readjusting cylinder 19.
  • the brake discs 50, 60 are rotatably mounted on a portion 37 of the shaft 1, which has a smaller diameter.
  • a first annular surface 38 is formed on which the brake disk 60 is axially supported.
  • a second annular surface 39 which serves to support the brake disc 50, is formed on a threaded nut 36, wherein the axial support of the brake disc 50 takes place on the second annular surface 39 via a compression spring 35.
  • the compression spring 35 which holds the mechanism together and the brake discs 50, 60 in position, also causes their return to the starting position, in which no spreading takes place.
  • a tension spring not shown, between the brake discs 50, 60 may be arranged.
  • the gears 30, 40 are engaged with toothed rings 33, 31 in engagement with the interposition of elements 34, 32 for thermal decoupling at the opposite axially inner surfaces of the brake discs 50, 60 attached are.
  • the said elements can be formed, for example, by webs that limit ventilation slots.
  • the attached to the disc 60 gear ring 31 is provided on the sides with a wall ring 42 which dips into a groove in the ring 2 and protects the mechanism from contamination.
  • the braking and the releasing operation take place in the second embodiment shown in FIGS. 5 to 7 substantially comparable to those of the first embodiment according to the variant 1.
  • the two brake disks 50, 60 rotate synchronously, so that no relative rotation of the brake disks 50, 60 relative to one another and thus no adjustment of the gears 30, 40 takes place.
  • the difference between the minimum and maximum dimensions of the oval cross-section of the gears 30, 40 gives the magnitude of the change in the axial distance between the brake discs 50, 60, which are mutually synchronized by the oval gears 30, 40.
  • the mentioned difference can be chosen such that after a H-rotation of the gears 30, 40, the maximum spread is reached.
  • the design of the brake can be chosen so that this point is not exceeded in practical operation.
  • Fig. 8 shows a first embodiment of a second variant of the present invention, wherein both variants are based on the same functional principle.
  • only one brake disk 70 is provided here, so that advantageously a commercially available brake disk can be used, which is firmly connected to the shaft 1.
  • the friction linings 80, 90 movable in the direction of rotation of the brake disc 70, wherein in a braking operation caused by a mechanical coupling means 74 axial Movement of the friction linings (80, 90) takes place towards each other.
  • the coupling means are designed here as oval gears 74.
  • means for mutual synchronization of the friction linings 80, 90 are provided.
  • gear 71 which is mounted for example by means of a cylindrical pin 73 in the brake caliper 7.
  • the gear 71 engages on one side in a mounted on the base plate of the friction lining 90 teeth and on the other side in the teeth of a Nachstellschiene 72, which is toothed in the direction of rotation of the brake disc 70 with the base plate of the friction lining 80.
  • the base plate of the friction lining 80 engages, for example, in the direction of the axis of rotation extending groove or grooves, which allows a free movement of the friction lining 80 for adjustment and Lsymmetricspielbergerwindung.
  • the adjustment is designated in FIG. 8 by the letter "N" and will be explained in more detail in connection with FIG. 9.
  • the friction linings 80, 90 are movably guided in the direction of rotation of the brake disk 70 and mounted to the caliper 7 on the back of the base plates via gears 74.
  • the gears 74 are in particular made oval and serve as a mechanical coupling means. Conceivable here would be another coupling, for example via round gears and sloping or rising ramps, as described above in connection with variant 1.
  • According to the invention takes place in the second variant in a braking operation caused by mechanical coupling means 74, 82, 83 axial movement of the friction linings 80, 90 towards each other.
  • By movement of the friction linings 80, 90 so the spreading takes place.
  • Oval gears 74 the long side of the oval to the brake disc 70 acts.
  • Fig. 9 shows in detail the adjusting mechanism.
  • the adjustment rail 72 engages the gear 73.
  • the base plate of the friction lining 80 engages in the groove (s) extending in the direction of the axis of rotation, which allows free movement of the friction lining 80 for adjustment and overcoming of clearance.
  • Fig. 10 the principle of operation of the mutual synchronization (without adjustment function) is shown schematically. In rest position (brake released), it is advisable to dispose the friction linings 80, 90 offset. Only when applying you will be in the range of max. Clamping force of the caliper 7 congruent.
  • FIG. 11 and FIG. 12 show an alternative to the spreading or mechanical coupling of the friction linings 80, 90.
  • the respectively illustrated contour is selected here in cooperation with an abutment 81. Since a maximum of one H rotation of the component 82 takes place, a completely circumferential toothing is not required. The gearing can possibly be omitted or reduced. Again, several variants are possible again. Either, as shown in Fig. 11 top right, the radius increases. Or, as in the bottom left of Fig. 11, by a ramp - or a combination of both.
  • FIG. 12 shows a geometric contour 83 in which the maximum spread takes place after an H rotation. Other variants and geometric contours are conceivable here. In Fig.
  • a regulation of the braking force and the adjustment can be carried out in both variants and their embodiments, for example by means of an electronic current regulator shown in Fig. 14, which can vary the electric current in time / strength and direction of the coil of the actuator 17 to two or four wheels is supplied.
  • As input variables for the current controller are control signals from various sensors, eg. B. each a wheel or speed sensor on each brake disc 50, 60, 70. By evaluating the phase position in the controller, the relative position of the brake discs 50, 60 are derived from each other.
  • sensors for detecting the position of the brake discs, for detecting the force applied by the caliper clamping force or for detecting the direction of travel can be used.
  • position sensors for detecting the positions of the friction linings 80, 90 are conceivable.
  • the setpoint can be determined, for example, from the pedal operation.
  • the actuator 10 may also perform the function of a parking brake.
  • the brake discs 5, 6 are in the starting position.
  • the use of an electric motor with higher torque is conceivable.
  • Other alternatives are a smaller pitch of the threads of the Nachstellzylinders in Brake caliper or a reduction in the friction occurring in the threads by using bearings or lubricants.
  • a release of the parking brake in an emergency or in case of failure of the electrical power supply can be done by a mechanical release of the adjusting cylinder 19, for example by means of a suitable tool.
  • the guide pins are mounted a few degrees different to the right angle with respect to the direction of rotation of the.
  • a braking force and brake discs releases a force towards guide pins.
  • the actuator could also be connected to the Guide pins attached another component, eg. B. a metal plate, begin.
  • materials with low thermal conductivity eg. As ceramics, carbon fiber, etc. are used.
  • the toothed rings can be superimposed on a waveform having an amplitude of approximately 0.5 mm in the course of the height. By the slope of the mentioned waveform, the self-amplification factor can be determined. A sinusoid initially gives a low gain and the highest gain just before the vertex. Thus, a lower force of the actuator 17 is required to generate the same braking force.
  • the present invention is characterized by an extremely good, wear-free controllability. To set and control no mechanical part (mass) must be moved, but only the force applied by the actuator 17 force to be changed. As a result, a very low power consumption is required.
  • the actuation of the actuator 17 can be done in terms of power by clocks, the direction of force is achieved by reversing.

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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 à réglage électrique, qui comporte un étrier monté flottant, au moins un disque de frein et une unité d'actionnement électrique destinée à appliquer une force agissant sur des garnitures de friction, l'une des garnitures de friction pouvant être amenée en contact avec le disque de frein directement par l'unité d'actionnement et l'autre garniture de friction par l'effet d'une force de réaction appliquée par l'étrier de frein. Selon l'invention, pour réduire la consommation d'énergie du frein, ledit frein à disque comporte soit deux disques de frein (5, 6, 50, 60) qui peuvent se déplacer axialement de manière limitée et qui peuvent tourner de manière limitée l'un par rapport à l'autre, un mouvement axial des disques de frein (5, 6, 50, 60) provoqué par des moyens mécaniques d'accouplement (3, 4, 15, 16, 21, 22; 30, 40, 31, 33) se produisant dans des directions opposées; soit des garnitures de friction (80, 90) mobiles dans le sens de rotation du disque de frein (70), un mouvement axial des garnitures de friction (80, 90) l'une vers l'autre, provoqué par des moyens mécaniques d'accouplement (74, 82, 83) se produisant alors.
PCT/DE2008/000795 2008-04-24 2008-04-24 Frein à disque à réglage électrique WO2009129764A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112008003923T DE112008003923A5 (de) 2008-04-24 2008-04-24 Elektrisch regelbare Scheibenbremse
PCT/DE2008/000795 WO2009129764A1 (fr) 2008-04-24 2008-04-24 Frein à disque à réglage électrique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/DE2008/000795 WO2009129764A1 (fr) 2008-04-24 2008-04-24 Frein à disque à réglage électrique

Publications (1)

Publication Number Publication Date
WO2009129764A1 true WO2009129764A1 (fr) 2009-10-29

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ID=40291286

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2008/000795 WO2009129764A1 (fr) 2008-04-24 2008-04-24 Frein à disque à réglage électrique

Country Status (2)

Country Link
DE (1) DE112008003923A5 (fr)
WO (1) WO2009129764A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3404281A1 (fr) * 2017-05-19 2018-11-21 Tüschen & Zimmermann GmbH & Co. KG Dispositif de fonctionnement d'un dispositif mécanique, en particulier d'un dispositif de freinage

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5219048A (en) * 1992-05-01 1993-06-15 General Motors Corporation Electric disc brake
EP1231401A2 (fr) * 2001-02-09 2002-08-14 Meritor Heavy Vehicle Systems, LLC Frein à disque auto-serreur
DE10149695A1 (de) * 2001-10-09 2003-04-24 Estop Gmbh Elektromechanische Schwimmsattelscheibenbremse mit Selbstverstärkung
EP1550816A2 (fr) * 2003-12-29 2005-07-06 ArvinMeritor Technology, LLC Mécanisme de frein avec auto-serrage stabilisé
DE102006049615A1 (de) * 2006-10-20 2008-05-21 Continental Teves Ag & Co. Ohg Elektrisch regelbare Scheibenbremse

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5219048A (en) * 1992-05-01 1993-06-15 General Motors Corporation Electric disc brake
EP1231401A2 (fr) * 2001-02-09 2002-08-14 Meritor Heavy Vehicle Systems, LLC Frein à disque auto-serreur
DE10149695A1 (de) * 2001-10-09 2003-04-24 Estop Gmbh Elektromechanische Schwimmsattelscheibenbremse mit Selbstverstärkung
EP1550816A2 (fr) * 2003-12-29 2005-07-06 ArvinMeritor Technology, LLC Mécanisme de frein avec auto-serrage stabilisé
DE102006049615A1 (de) * 2006-10-20 2008-05-21 Continental Teves Ag & Co. Ohg Elektrisch regelbare Scheibenbremse

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3404281A1 (fr) * 2017-05-19 2018-11-21 Tüschen & Zimmermann GmbH & Co. KG Dispositif de fonctionnement d'un dispositif mécanique, en particulier d'un dispositif de freinage

Also Published As

Publication number Publication date
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