WO2004020864A1 - Etrier de frein - Google Patents

Etrier de frein Download PDF

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Publication number
WO2004020864A1
WO2004020864A1 PCT/EP2003/008779 EP0308779W WO2004020864A1 WO 2004020864 A1 WO2004020864 A1 WO 2004020864A1 EP 0308779 W EP0308779 W EP 0308779W WO 2004020864 A1 WO2004020864 A1 WO 2004020864A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
piston
pressure
brake caliper
pressure chamber
Prior art date
Application number
PCT/EP2003/008779
Other languages
German (de)
English (en)
Inventor
Guntram Ott
Original Assignee
Evalor Anstalt
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 Evalor Anstalt filed Critical Evalor Anstalt
Priority to AU2003258583A priority Critical patent/AU2003258583A1/en
Publication of WO2004020864A1 publication Critical patent/WO2004020864A1/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
    • 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
    • F16D2121/02—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
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/10—Plural pistons interacting by fluid pressure, e.g. hydraulic force amplifiers using different sized 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
    • F16D2125/18—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
    • F16D2125/28—Cams; Levers with cams

Definitions

  • the invention relates to a brake caliper for gripping over a brake disc which is connected in a rotationally fixed manner to a vehicle wheel, comprising a housing, a piston arrangement with a first piston which is displaceably guided in the housing and which can be adjusted parallel to the disc axis by a service brake device of the vehicle, and with a parallel one in the housing second piston adjustable to the disc axis, which acts on a brake lining intended for bearing against the brake disc, the two pistons enclosing between them a pressure chamber which can be connected via a connecting channel to the pressure medium circuit of a pressure medium-operated auxiliary or parking brake device of the vehicle.
  • the brake caliper mentioned above can be used for both the service brake and the auxiliary or parking brake. If pressure medium is fed into the pressure chamber between the two pistons via a control valve, only the second piston is moved and the parking brake is thus actuated. If the service brake is to be actuated, the pressure in the pressure chamber is locked in via the control valve, so that the first and second pistons move synchronously together with the fluid column locked between them. A major advantage of this The solution is that the decrease in the brake pad is automatically compensated for by the fluid flowing into the pressure chamber. An additional readjustment of the brake is not necessary.
  • the invention has for its object to design a brake caliper of the type mentioned so that the danger described above can be avoided and the pressure in the pressure chamber between the two pistons can be locked in any case.
  • connection channel can be shut off depending on an actuation of the service brake.
  • connection channel is blocked when the service brake is actuated, so that no fluid can escape from the pressure space between the two pistons and the brake responds immediately or with only an insignificant delay.
  • the first piston delimits a further pressure space which can be connected to the pressure medium circuit of a pressure medium-operated service brake.
  • the connection channel can be shut off by a valve which is by the When the service brake is actuated and a pressure is built up in the pressure medium circuit of the service brake, the valve is immediately moved into its blocking position and the pressure is thus locked in the first pressure chamber between the two pistons.
  • the valve described above can be realized in a very simple manner in that it has a plunger which is arranged displaceably in a bore of the housing or an attached valve housing which intersects the connecting channel and is connected to a piston which is on its side facing away from the plunger Pressure of the pressure medium circuit of the service brake can be applied.
  • the valve tappet is preferably biased into the open position of the valve, so that it is ensured that the valve opens again when the service brake is released.
  • the design of the brake caliper described above is independent of whether the two pistons are arranged axially one behind the other or whether the second piston is guided telescopically in the first piston.
  • connection channel can be shut off by an electrically controllable valve which can be activated, for example, by the brake light switch.
  • the first piston is arranged such that it closes the mouth of the connecting channel into the pressure space between the two pistons when it is adjusted in the direction of the second piston.
  • the pressure in the pressure space between the two pistons is thus locked by the piston itself at the beginning of the movement of the first piston. Then the two pistons move together.
  • the pressure space present between the two pistons can be connected to a pressure medium source by means of a further channel, in the further channel preventing the pressure medium from flowing out of the pressure space Check valve is arranged and wherein the mouth of the Second channel in the pressure chamber is arranged and designed so that it remains open under all operating conditions.
  • the first piston can be adjusted hydraulically or also by a mechanical or electromechanical adjusting device.
  • the first piston has a smaller diameter than the second piston.
  • the connection channel can first be shut off by the first piston before the brake pressure is built up in the first pressure chamber, so that the risk is low that in the initial phase of actuating the service brake in the event of a leak in the pressure medium circuit of the parking brake, fluid from the pressure chamber can escape between the two pistons. Only when the first piston has shut off the connecting channel, has the second piston moved so far that the brake lining rests on the disk and thus the pressure in the pressure space between the two pistons increases. At this moment, however, the connection line is closed and the pressure in the pressure chamber is thus locked up.
  • the object on which the invention is based can also be achieved in the case of a brake caliper of the type mentioned at the outset in that the pistons are arranged axially one behind the other and in that the first piston is prestressed in the direction of the second piston by spring means, the prestressing force being less than the restoring force, which acts in the brake-free state on the first and / or second piston in the sense of lifting the brake pad from the brake disc.
  • This solution is particularly advantageous in the event that the pressure between the two pistons escapes only gradually via a small leak.
  • the first piston is automatically adjusted until it mechanically abuts the second piston so that the service brake can respond immediately.
  • FIG. 1 shows a schematic section through the piston axis through a brake caliper for a brake device with a hydraulically actuated service and parking brake
  • FIG. 2 shows an enlarged section through the valve for shutting off the connecting channel
  • Figure 3 shows a section corresponding to Figure 1 through a modified
  • Figure 4 is a representation corresponding to Figure 3 of a modified
  • FIG. 5 shows a schematic illustration of a further embodiment of a hydraulically actuated brake caliper
  • FIGS. 3 to 5 shows a representation corresponding to FIGS. 3 to 5 of a brake caliper with a mechanically displaceable first piston and a hydraulically displaceable second piston and
  • Figure 7 is a schematic representation of a brake caliper according to another aspect of the present invention.
  • FIG. 1 one can see a brake caliper, generally designated 10, with a Zan ⁇ teil 12. which overlaps a brake disc 14. Within the tooth part 12 one connected to the pliers part 12 and the other slidably mounted parallel to the axis A of the brake disc 14.
  • a housing 18 is connected to a piston bore 20 in which a first piston 22 is slidably mounted parallel to the axis A.
  • a service brake device i.e. pressure on the brake pedal of the vehicle.
  • fluid is pumped into the pressure chamber 26
  • the first piston 22 is shifted to the right in FIG. 1 and presses the left brake pad 16 in FIG. 1 against the brake disc 14. Since the housing 18 receiving the pressure chamber 26 is rigidly connected to the brake caliper 12, at the same time the right brake pad 16 in FIG.
  • the brake disc 14 is clamped like pliers between the two brake pads 16. If the pressure chamber 26 is depressurized, i.e. released the brake pedal, the first piston 22 is reset by an elastic ring 33 which is held in a groove 35 in the wall of the piston bore 20 and is elastically deformed when the first piston 22 is moved in the direction of the brake disc.
  • the first piston 22 is cup-shaped and accommodates a second piston 30 which is telescopically displaceable in it and which is likewise displaceable parallel to the axis A and is intended for contact with the brake lining 16.
  • a further pressure chamber 36 is formed, which can be connected via a connection channel 38 to a pressure medium circuit, not shown, of a parking brake device. If the fluid pressure in the pressure chamber 36 is increased by actuating the parking brake device, the second piston 30 is shifted to the right in FIG. 1 and presses the brake pad 16 against the brake disc 14 in the same manner as was described for the first piston 22. The pressure is normally locked in the pressure medium circuit of the parking brake.
  • the first and second pistons 22 and 30 move together with the fluid column locked between them, as if the two pistons were rigidly connected to one another. If a leak now occurs in the pressure medium circuit of the parking brake, for example tearing off the brake hose or the brake line leading to the connecting channel 38, there is a risk that when the service brake is actuated, the first piston 22 is displaced and not the piston 30 via the between takes them lying fluid column, but pushes the fluid out of the pressure chamber 36 through the connection channel 38. In this case, the travel of the first piston 22 may be extended until the brake is activated. In order to prevent this danger, a valve 40 is provided in order to be able to shut off the connecting channel 38.
  • the valve 40 comprises a block-shaped valve housing 42 attached to the housing 18 and having bores 44 and 46 aligned with the channels 28 and 38.
  • the two bores 44 and 46 are connected to one another by a valve bore 48, which widens in a central section to form a piston chamber 50.
  • the valve body of the valve 40 comprises a tappet 52, the diameter of which corresponds to the diameter of the valve bore 48.
  • the tappet is connected at its end facing the bore 44 to a piston 54 which can be acted upon by the operating pressure of the pressure medium of the service brake system, ie the brake pressure.
  • the plunger can be moved from the position shown in FIG. 1 to the right so far that it closes the bore 46 and thus also closes off the connecting channel 38.
  • FIG. 1 In the enlarged illustration in FIG.
  • connection piece 56 is screwed into the bore 46 and is used to connect a fluid line of the pressure medium circuit of the parking brake device.
  • an orifice plate 58 is inserted, the orifice opening 60 of which can be selected so that fluid from the pressure chamber 36 cannot run out automatically but can only be pushed out by pressure when a leak occurs in the pressure medium circuit of the parking brake.
  • the plunger 52 and the piston 54 are biased to the left by a helical compression spring 62 in FIGS. 1 and 2, that is to say in the release or open position of the valve 40. As a result, the valve 40 always opens when the pressure spaces 26 and 36 are depressurized.
  • the piston 54 is pressurized, as a result of which the valve tappet 52 is displaced to the right in FIGS. 1 and 2, so that it blocks the connecting channel 38. This ensures in any case that the pressure remains locked in the pressure chamber 36 and the two pistons 22 and 30 move synchronously, possibly with a slight delay.
  • FIG. 3 shows a modified embodiment of the brake caliper, the same parts having the same effect being identified by the same reference numerals as in FIG. 1.
  • the embodiment according to FIG. 3 differs from that of FIG. 1 only in that the first and the second pistons 22 and 30 are not guided telescopically one inside the other but lie axially next to one another. It can be clearly seen in this exemplary embodiment that in the event that the pressure in the pressure chamber 36 cannot be locked in, the first piston 22 can only exert pressure on the brake lining 16 when it strikes the second piston 30 and thus the second Piston 30 mechanically adjusted. Otherwise, the brake caliper according to FIG. 3 operates in the same way as that of FIG. 1.
  • Figure 4 shows a brake caliper similar to that of Figure 3, wherein the same parts are again designated by the same reference numerals.
  • the brake caliper according to FIG. 4 differs from that of FIG. 3 in that the valve 40 is electrically controllable and adjustable between a passage position shown in FIG. 4 and a blocking position.
  • the control can take place via a brake light switch 59, which can be actuated by a brake pedal 61 and normally switches on a brake light 63. Otherwise, the brake caliper according to FIG. 4 works in the same way as that of FIG. 3.
  • FIGS. 5 and 6 show two variants of a further embodiment of a brake caliper according to the invention, the same parts again being identified with the same reference numerals.
  • first piston 22 is hydraulically adjusted in a manner known per se.
  • the first piston is adjusted parallel to the disk axis A via a cam or eccentric disk 64.
  • the eccentric disk 64 is adjusted by an electric motor, not shown, for example a stepper motor.
  • the first piston is not arranged coaxially with the second piston 30 and has a diameter which is substantially smaller than this.
  • the first piston simultaneously serves as a valve element, which can shut off the connection channel 38, which connects the pressure chamber 36 to the pressure medium circuit of the parking brake. If the service brake is actuated and the first piston 22 is shifted to the right via the eccentric disk 64 in FIG. 6, the piston 22 firstly shuts off the connecting channel 38, as shown in FIG. 6. At this moment, no more fluid can escape from the pressure chamber 36. When the piston 22 is moved further to the right in FIG. 6, the second piston 30 is taken along with the corresponding hydraulic transmission ratio.
  • connection channel 38 there is another hole; 66 a check valve 68 is arranged, which allows an inflow of pressure medium to the pressure chamber 36, but prevents the pressure medium from escaping from the pressure chamber 36.
  • the mouth of the bore 66 in the pressure chamber 36 is designed so that it is open under all operating conditions. By supplying pressure fluid to the pressure chamber 36, the brake can be released again if a leak has occurred in the pressure medium line to the connection channel 38 and the first piston 22 has therefore blocked the mouth of the connection channel 38 when the service brake is actuated.
  • FIG. 7 finally shows a variant of a brake caliper which is constructed essentially as the brake calipers shown in FIGS. 3 and 4, but the valve 40 can be omitted.
  • a spring 70 is arranged in the pressure chamber 26 and biases the first piston 22 in the direction of the brake disc 14. If there is a leak in the supply line to the connecting duct 38, even if it is only a very small leak, then the spring 20 presses the first piston 22 in the direction of the brake disk 14 in accordance with the escape of the pressure fluid, until the first piston 22 on the second piston 30 strikes. The service brake is thus immediately ready for operation when actuated.

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

Abstract

L'invention concerne un étrier de frein destiné à chevaucher un disque de frein (14) solidaire en rotation d'une roue de véhicule. Cet étrier comprend un boîtier (18) et un ensemble de pistons (22, 30) constitué d'un premier piston (22), guidé de façon coulissante dans le boîtier (18) et pouvant être déplacé parallèlement à l'axe (A) du disque par l'intermédiaire d'un système de freinage de service du véhicule, et d'un second piston (30), pouvant être déplacé dans ce boîtier (18) parallèlement à l'axe (A) du disque et agissant sur une garniture de frein (16) conçue pour venir appuyer contre le disque de frein (14), lesquels pistons (22, 30) renferment une chambre de pression (36) pouvant être reliée au circuit de fluide sous pression d'un frein auxiliaire ou d'arrêt commandé par pression dudit véhicule par l'intermédiaire d'un canal de raccordement (38). Selon la présente invention, ce canal de raccordement (38) est obturable en fonction d'un actionnement du frein de service.
PCT/EP2003/008779 2002-08-09 2003-08-07 Etrier de frein WO2004020864A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003258583A AU2003258583A1 (en) 2002-08-09 2003-08-07 Brake caliper

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002136686 DE10236686A1 (de) 2002-08-09 2002-08-09 Bremszange
DE10236686.1 2002-08-09

Publications (1)

Publication Number Publication Date
WO2004020864A1 true WO2004020864A1 (fr) 2004-03-11

Family

ID=30469675

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/008779 WO2004020864A1 (fr) 2002-08-09 2003-08-07 Etrier de frein

Country Status (3)

Country Link
AU (1) AU2003258583A1 (fr)
DE (1) DE10236686A1 (fr)
WO (1) WO2004020864A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004045846A1 (de) 2004-09-20 2006-03-23 Faiveley Transport Remscheid Gmbh Vorrichtung und Verfahren zur Überwachung der Funktion einer Bremszange
JP4650434B2 (ja) 2007-01-26 2011-03-16 トヨタ自動車株式会社 ディスクブレーキ装置
CN112145582B (zh) * 2019-06-28 2021-11-12 比亚迪股份有限公司 盘式制动器、线控制动系统以及车辆

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3312313A (en) * 1965-06-23 1967-04-04 Bendix Corp Independently operable dual brake actuating apparatus
US3773148A (en) * 1971-03-19 1973-11-20 B A Paris Sa D Hydraulic brake actuator for a disc brake
US4412603A (en) * 1981-12-28 1983-11-01 Goodyear Aerospace Corporation Dual pressure, dual piston actuator
EP0169178A2 (fr) * 1984-07-11 1986-01-22 FIAT AUTO S.p.A. Etrier de sécurité pour un frein à disque de véhicules à moteur

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3312313A (en) * 1965-06-23 1967-04-04 Bendix Corp Independently operable dual brake actuating apparatus
US3773148A (en) * 1971-03-19 1973-11-20 B A Paris Sa D Hydraulic brake actuator for a disc brake
US4412603A (en) * 1981-12-28 1983-11-01 Goodyear Aerospace Corporation Dual pressure, dual piston actuator
EP0169178A2 (fr) * 1984-07-11 1986-01-22 FIAT AUTO S.p.A. Etrier de sécurité pour un frein à disque de véhicules à moteur

Also Published As

Publication number Publication date
DE10236686A1 (de) 2004-02-19
AU2003258583A1 (en) 2004-03-19

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