EP0741652A1 - Systeme de freinage hydraulique a regulation antipatinage - Google Patents

Systeme de freinage hydraulique a regulation antipatinage

Info

Publication number
EP0741652A1
EP0741652A1 EP95907607A EP95907607A EP0741652A1 EP 0741652 A1 EP0741652 A1 EP 0741652A1 EP 95907607 A EP95907607 A EP 95907607A EP 95907607 A EP95907607 A EP 95907607A EP 0741652 A1 EP0741652 A1 EP 0741652A1
Authority
EP
European Patent Office
Prior art keywords
magnetic core
valve
brake system
sealing seat
pressure line
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
EP95907607A
Other languages
German (de)
English (en)
Inventor
Helmut Weis
Klaus-Diether Fischer
Peter Volz
Dalibor Zaviska
Paul Linhoff
Ralf Kaiser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co OHG
Original Assignee
ITT Automotive Europe GmbH
Alfred Teves GmbH
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 DE4403295A external-priority patent/DE4403295A1/de
Application filed by ITT Automotive Europe GmbH, Alfred Teves GmbH filed Critical ITT Automotive Europe GmbH
Publication of EP0741652A1 publication Critical patent/EP0741652A1/fr
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B60T8/365—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems combining a plurality of functions in one unit, e.g. pressure relief
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems
    • B60T8/5037—Pressure reapplication using restrictions in hydraulic brake systems closed systems
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S303/00—Fluid-pressure and analogous brake systems
    • Y10S303/90—ABS throttle control
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87917—Flow path with serial valves and/or closures
    • Y10T137/88046—Biased valve with external operator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87917—Flow path with serial valves and/or closures
    • Y10T137/88062—Coaxial oppositely directed seats

Definitions

  • the invention relates to a hydraulic brake system with slip control according to the preamble of claim 1 and represents a further embodiment of the subject matter of the invention according to a patent (patent application file number: P 43 19 227.0).
  • the discontinuous pressure medium control in slip-controlled brake systems by means of digitally switchable inlet and outlet valves leads to undesired noise emission due to the pulse-like pressure curve.
  • the annular space originally accommodating an annular filter and the valve closing member advantageously serves at the same time for integrating the annular piston and the diaphragm, with which the external dimensions of the valve carrier and the dimensions of the step bore of the valve receiving body can be maintained.
  • the ring area between the valve receiving body and the valve carrier can be used to arrange the ring filter, which results in an advantageous enlargement of the filter area for filtering the u.a. fluid also flows between the wheel brake and the non-return sleeve.
  • FIG. 1 is a partial view of an intake valve in an enlarged view, with the arrangement of the annular piston according to the invention in the region of the valve closing member,
  • FIG. 2 shows a cross section of the inlet valve according to FIG. 1, at point A-A of the valve carrier, on an enlarged scale.
  • FIG. 1 shows a constructive exemplary embodiment for the overall structure of the inlet valve 1.
  • the inlet valve 1 has a valve carrier 10 which contains the valve closing member 11 and the channel guide of the main pressure line 2 coming from the brake pressure transmitter 5 and the auxiliary pressure pump 18.
  • the valve support 10 is preferably integrated in a cartridge design (screw-in cartridge, caulking cartridge, cartridge with expansion ring) in a valve receiving body 9.
  • the valve carrier 10 is fastened in the conically tapered outer area with an expansion ring 128 in the valve receiving body 9, the opening for receiving the expansion ring 128 is provided with a conical undercut.
  • valve carrier 10 The sealing of the valve carrier 10 in the valve receiving body 9 is ensured by a seal arranged below the conically shaped valve carrier 10.
  • the annular piston 8 takes over the switchable diaphragm function as a result of a transverse bore in the annular piston wall. This is on the reduced-diameter extension of the rotationally symmetrical central valve valve 116 body 114 in the annular space 126 axially movable.
  • the annular piston 8 is supported under the action of a compression spring 7 with its outer collar 119, which acts as a stop, on the bore step of the annular space 126 in the valve carrier 10.
  • the ring piston 8 essentially has the shape of a sleeve, which is provided on its end face facing the magnetic core 127 with a funnel-shaped rubber sealing seat 115, which lies opposite the conically shaped end region of the magnetic core 127.
  • the cone seal can also be designed as a metallic flat seal or with an O-ring enclosed in the end face area of the annular piston 8.
  • a sealing ring 124 which, in the closed position of the inlet valve 1, prevents pressure medium from flowing over from the brake pressure transmitter 5 in the direction of the wheel brake 3.
  • the rotationally symmetrical central body 114 which extends into the interior with its extension, is pressed into the stepped bore of the valve carrier 10 and, if necessary, caulked in the end face region.
  • the valve seat 116 is pressed as a stepped sleeve part into the bore of the central body 114 which runs coaxially with the valve closing member 11.
  • FIG. 2 shows a top view of the inlet valve 1 shown in FIG.
  • the central body 114 through the execution as a square profile, has correspondingly large pressure medium passages in the direction of the annular piston 8 relative to the inner wall of the valve support 10 upstream sealing ring 124.
  • the sectional plane penetrates the lower end section of the valve carrier 10, on which the plate filter 21 is clipped on.
  • the plate filter 21 has several recesses 120 distributed over the circumference, which allow the pressure medium to pass from the direction of the sealing sleeve 112. All the elements described for the section plane AA are thus in a rotationally symmetrical coaxial arrangement with respect to one another.
  • FIG. 3 likewise shows valve seat 116 integrated as a homogeneous component in central body 114 on a considerably enlarged scale, so that the separate arrangement of a further sleeve-shaped press-in part having valve seat 116 explained in FIG. 1 is omitted.
  • a fixed end 31 is additionally pressed in the valve carrier 10 as an insert into the transverse bore 13 of the valve carrier 10 hydraulically connecting the annular space 126 to the wheel brake 3, and if necessary, correspondingly the Representation in FIG. 1, the function of the fixed orifice is also possible by calibrated fine drilling of the transverse bore.
  • the valve support 10 is by means of a Receiving body 9 held self-inserting attachment, so that the sealing ring known from Figure 1 can be dispensed with.
  • both the end face of the magnetic core 127 forming the sealing seat 115 and the end face of the annular piston 8 forming the sealing seat 115 are designed exclusively as flat metal seals, the sealing seat 115 on the annular piston 8 is designed as a blade-shaped web 200 which likewise takes over the function of the diaphragm 4 by means of a notch 204.
  • the indentation can be produced inexpensively, for example by milling, punching, eroding and, due to its peripheral arrangement, prevents contamination or blockage in comparison to the previously known aperture bores.
  • a self-cleaning effect of the notch 204 inevitably occurs during the restoring movement of the annular piston 8 which releases the sealing seat 115.
  • FIG. 5 shows an enlarged, alternative embodiment for sealing an annular piston by combining a metallic sealing seat 115 on the annular piston 8 with an elastically deformable sealing seat 115 on the magnetic core 127.
  • the sealing seat 115 on the magnetic core 127 is made of PTFE or EPDM plastics.
  • the elastic sealing seat 115 has a groove-shaped annular groove 201.
  • the seal forming the sealing seat 115 is clamped in the magnetic core 127 by the ring web 205 projecting on the end face of the magnetic core 127 after being inserted. the seal is pressed in.
  • the ring seal is preferably made of polytetrafluoroethylene (PTFE) and, with its free sealing seat surface, faces the sealing ring 115 on the ring piston 8, which is essentially circumferential in a ring shape.
  • the aperture 204 is attached as a notch to the annular sealing seat 115.
  • the sealing seat 115 of the annular piston 8 according to FIG. 7 differs from the embodiment according to FIG. 6 primarily by a large, flat sealing seat, so that a reduction in cross-section in the groove-shaped notched aperture 4 is avoided when the elastic seal 115 is put on .
  • the elastic seal 115 and its fastening in the magnetic core 127 correspond to the previous embodiment according to FIG. 6.
  • FIG. 8 A further expedient possibility for fastening the elastic seal 115 on the magnetic core 127 can be seen in FIG. 8.
  • the elastomeric sealing material is injected into the cavity located in the undercut 202 in the magnetic core 127 and is held in a force-fitting manner by the sleeve 203 which extends coaxially to the valve tappet into the cavity of the elastomeric sealing element.
  • the sleeve 203 is inserted as a plug-in part from above into the stepped bore of the magnetic core 127 and is fixed via its collar on the bore step by the compression spring resting on the magnet armature.
  • the sealing seat 115 is formed exclusively from metallic sealing surfaces, with the special feature that the diaphragm 4 consists of a spiral-shaped groove embedded in the end face of the magnetic core 127, which is produced, for example, during machining a turning tool retraction movement can be produced simply, precisely and inexpensively.
  • the overall representation of the spiral groove is evident from the plan view shown in FIG. 10 of the interface A marked in FIG. 9.
  • FIG. 11 shows an alternative fastening measure for the elastomeric sealing element within a separate holding part 206 positioned between the magnetic core 127 and the valve support 10.
  • the sealing element is preferably vulcanized into the metallic holding part 206 and additionally by means of positive edges within the holding part secured.
  • the essentially disk-shaped holding part 206 enables the further components arranged below the holding part to be preassembled and facilitates the adjustment of the valve tappet stroke.
  • the elastomeric sealing material is injected from the side facing away from the sealing seat surface, so that the formation of an injection burr in the region of the sealing seat 115 is reliably avoided.
  • the inlet valve 1 is in the open, non-energized, open basic position.
  • the brake pressure sensor 5 is actuated, there is no back pressure in the valve inlet of the inlet valve 1, since the valve seat 116 does not cause any significant throttling or orifice effect, which means that by no significant pressure difference between the valve inlet and valve outlet.
  • the annular piston 8 remains in the initial position at the bore step at the stop, so that the brake pressure can act on the wheel brake 3 via the valve seat 116 and via the annular gap between the annular piston 8 and the magnetic core 127.
  • valve inlet valve 1 when the inlet valve 1 is closed, the pressure difference between the valve inlet (master cylinder / pump pressure) and valve outlet (wheel brake pressure) exceeds a value set by the compression spring 7 during a brake slip control, the annular piston 8 is displaced against the spring force as a result of the resulting pressure force on the sealing ring 124 and comes into contact with the 127 magnetic core.
  • a pressure medium connection to the wheel brake 3 thus exists exclusively via the orifice 4 of the annular piston 8.

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)

Abstract

L'invention concerne un système de freinage à régulation antipatinage comprenant des soupapes d'admission et de sortie (1, 17) électromagnétiques à commutation numérique. Une commande à soupapes à diaphragme dépendant des pressions différentielles est associée à la soupape d'admission (1), afin de réduire les bruits des soupapes.
EP95907607A 1994-02-03 1995-01-25 Systeme de freinage hydraulique a regulation antipatinage Ceased EP0741652A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4403295 1994-02-03
DE4403295A DE4403295A1 (de) 1993-06-09 1994-02-03 Hydraulische Bremsanlage mit Schlupfregelung
PCT/EP1995/000264 WO1995021081A1 (fr) 1994-02-03 1995-01-25 Systeme de freinage hydraulique a regulation antipatinage

Publications (1)

Publication Number Publication Date
EP0741652A1 true EP0741652A1 (fr) 1996-11-13

Family

ID=6509375

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95907607A Ceased EP0741652A1 (fr) 1994-02-03 1995-01-25 Systeme de freinage hydraulique a regulation antipatinage

Country Status (4)

Country Link
US (1) US5803556A (fr)
EP (1) EP0741652A1 (fr)
JP (1) JPH09511468A (fr)
WO (1) WO1995021081A1 (fr)

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JP3905122B2 (ja) * 1993-09-28 2007-04-18 アイティーティー・オートモーティブ・ヨーロップ・ゲーエムベーハー スリップ制御付き液圧ブレーキシステム
DE19604317A1 (de) * 1996-02-07 1997-08-14 Bosch Gmbh Robert Elektromagnetisch betätigtes Ventil, insbesondere für hydraulische Bremsanlagen von Kraftfahrzeugen
DE19604315A1 (de) * 1996-02-07 1997-08-14 Bosch Gmbh Robert Elektromagnetisch betätigtes Ventil, insbesondere für hydraulische Bremsanlagen von Kraftfahrzeugen
JP3598409B2 (ja) * 1996-09-10 2004-12-08 日清紡績株式会社 液圧ブレーキ装置における液圧制御弁装置
JP3551221B2 (ja) * 1996-09-10 2004-08-04 日清紡績株式会社 液圧ブレーキ装置における液圧制御弁装置
US6276764B1 (en) * 1998-11-17 2001-08-21 Mando Machinery Corporation Solenoid valve for anti-lock brake system
DE19956821A1 (de) * 1998-11-30 2000-05-31 Denso Corp Elektromagnetisches Ventil für die Bremshydraulikdruck-Steuerung und Fahrzeugbremssteuersystem hiermit
JP2000309259A (ja) * 1999-04-26 2000-11-07 Nisshinbo Ind Inc 電磁弁装置
KR100423646B1 (ko) * 2000-07-18 2004-03-22 주식회사 만도 안티록 브레이크 시스템용 노말 오픈형 솔레노이드밸브
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DE10040763A1 (de) * 2000-08-19 2002-02-28 Bosch Gmbh Robert Elektromagnetisch betätigtes Ventil, insbesondere für hydraulische Bremsanlagen in Kraftfahrzeugen
US6634722B1 (en) * 2001-07-31 2003-10-21 Kelsey-Hayes Company Vehicle braking system with proportional poppet valve pressure control strategy
DE10252231A1 (de) * 2002-04-26 2003-11-06 Continental Teves Ag & Co Ohg Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeugbremsanlagen
US6846408B2 (en) * 2003-03-07 2005-01-25 Kelsey-Hayes Company Filter assembly for a control valve in a vehicular brake system
US7182413B2 (en) * 2003-06-13 2007-02-27 Kelsey-Hayes Company Valve seat for a control valve in a vehicle brake system
DE102005044672A1 (de) * 2005-09-19 2007-03-22 Robert Bosch Gmbh Magnetventil
DE102006003252A1 (de) * 2006-01-24 2007-07-26 Robert Bosch Gmbh Magnetventil
WO2008097534A1 (fr) * 2007-02-05 2008-08-14 Kelsey-Hayes Company Unité de commande hydraulique pour système de frein de véhicule
DE102007007784B4 (de) * 2007-02-16 2019-01-24 Robert Bosch Gmbh Magnetventil
US8267334B2 (en) * 2007-10-11 2012-09-18 Mando Corporation Solenoid valve for brake system
US20190077388A1 (en) * 2017-09-11 2019-03-14 Mando Corporation Solenoid valve for brake system
KR102079023B1 (ko) * 2017-11-06 2020-02-19 주식회사 만도 일체형 솔레노이드밸브 및 그를 이용한 브레이크 시스템
KR101996853B1 (ko) * 2018-03-14 2019-07-08 주식회사 만도 솔레노이드밸브
DE102019106498B4 (de) * 2019-03-14 2022-04-21 Schaeffler Technologies AG & Co. KG Vorgesteuertes Kühlmittelventil
DE102020213996A1 (de) 2020-11-06 2022-05-12 Continental Teves Ag & Co. Ohg Elektrohydraulische Bremsanlage für Kraftfahrzeuge

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Also Published As

Publication number Publication date
WO1995021081A1 (fr) 1995-08-10
JPH09511468A (ja) 1997-11-18
US5803556A (en) 1998-09-08

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