+

WO1997028031A1 - Systeme de freinage hydraulique a regulation antipatinage comportant une pompe d'amorçage - Google Patents

Systeme de freinage hydraulique a regulation antipatinage comportant une pompe d'amorçage Download PDF

Info

Publication number
WO1997028031A1
WO1997028031A1 PCT/EP1997/000285 EP9700285W WO9728031A1 WO 1997028031 A1 WO1997028031 A1 WO 1997028031A1 EP 9700285 W EP9700285 W EP 9700285W WO 9728031 A1 WO9728031 A1 WO 9728031A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
connection
pressure
brake
charge pump
Prior art date
Application number
PCT/EP1997/000285
Other languages
German (de)
English (en)
Inventor
Helmut Steffes
Original Assignee
Itt Manufacturing Enterprises, Inc.
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 Itt Manufacturing Enterprises, Inc. filed Critical Itt Manufacturing Enterprises, Inc.
Priority to JP9527275A priority Critical patent/JP2000503933A/ja
Priority to EP97901582A priority patent/EP0874748A1/fr
Publication of WO1997028031A1 publication Critical patent/WO1997028031A1/fr

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
    • B60T8/48—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 connecting the brake actuator to an alternative or additional source of fluid pressure, e.g. traction control systems
    • B60T8/4809—Traction control, stability control, using both the wheel brakes and other automatic braking systems
    • B60T8/4827—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems
    • B60T8/4863—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems
    • B60T8/4872—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems pump-back systems
    • B60T8/4881—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems pump-back systems having priming means
    • 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
    • B60T8/341—Systems characterised by their valves

Definitions

  • the present invention is based on a slip-controlled hydraulic brake system according to the preamble of claim 1.
  • brake systems are known, for example, from DE 42 32 311 Cl and from DE 43 29 139 Cl. In both cases, these are brake systems which are suitable both for brake slip control and for automatic brake actuation.
  • During a brake slip control they operate according to the return feed principle.
  • the two return pumps of the anti-lock control are used as pressure sources for the automatic activation of the wheel brakes.
  • precharge cylinders designed in the manner of single-circuit master cylinders are provided, the trailing chambers of which are connected to a pressure outlet of the pedal-operated master cylinder.
  • the pressure outputs of the precharge cylinders can be connected to the brake line of each brake circuit and to the suction side of its return pump by means of a control valve arrangement.
  • the pressure outputs of the return pumps are shut off against the pressure outputs of the precharge cylinders and the latter on the suction sides of the by switching the control valve arrangement Return pumps connected.
  • the precharge cylinders are both actuated by a common charge pump, which acts on the piston surfaces of the precharge cylinder with their delivery pressure.
  • the suction side of the charge pump is connected to the reservoir.
  • a seat valve is closed by the pressure of the charge pump, which blocks the connection from the pedal-operated master cylinder to the wheel brakes.
  • the precharge cylinders of the two publications differ in that DE 42 32 311 Cl has two separate precharge cylinders, each with a drive pressure chamber, the drive pressure chambers being connected to the charge pump via a common pressure line, while in DE 43 29 139 the Both precharge cylinders have a common, centrally arranged drive pressure chamber, which is connected to the pressure side of the charge pump. As a result, the corresponding pistons of this precharging device move apart as soon as the charge pump builds up pressure.
  • the object of the present invention is to provide a brake system according to the preamble of claim 1 when using a common pump for precharging the return pumps, in which two separate static brake circuits are retained in accordance with the statutory provisions and are inexpensive while maintaining closed circuits static brake circuits there is the possibility of pre-charging.
  • the principle of the present invention is to arrange the charge pump above the master cylinder and to block the connection between the master cylinder and the reservoir by means of a hydraulically operated switching valve.
  • the switching valve has two active surfaces: the delivery pressure of the charge pump acts directly on the first active surface in the closing direction and, after overcoming a non-return valve on the part of the follow-up connection of the master cylinder, in the opening direction on the second active surface.
  • the pressure acting in the closing direction is always greater than the pressure acting in the opening direction and reduced by the admission pressure of the check valve, as long as the isolating valve in the brake line remains closed.
  • the isolating valve When an active braking is ended, the isolating valve is opened so that the brake pressure propagates through the unactuated master cylinder to the switching valve and opens it.
  • An electronic control logic and electrical lines to the switching valve are therefore not required.
  • Such an arrangement of the charge pump above the master cylinder is not limited to brake systems in which precharging is required in both brake circuits, but can also be used for brake systems in which only the return pump of a brake circuit needs to be precharged .
  • the return pump is optimized for achieving high delivery pressures and can therefore only deliver a comparatively small volume flow.
  • the charge pump delivers a maximum volume flow at low pressures. This is particularly important when initiating an automatic braking process if the air clearances of the wheel brakes in question must first be overcome. This applies to both self-priming and non-self-priming return pumps.
  • FIG. 1 shows a brake system according to the invention with a hydraulically actuated switching valve, only the trailing space of the first brake circuit being precharged
  • FIG. 2 shows a constructive solution for a hydraulically operated switching valve according to FIG. 1.
  • the brake line 3 runs from the master cylinder 1 via an electromagnetically actuated, normally open isolating valve 4 and is divided into two brake branches 5 and 6.
  • the brake branch 5 leads via the electromagnetic actuated, normally open inlet valve 7 to the wheel brake 8, while the brake branch 6 leads via a likewise normally open, electromagnetically operated inlet valve 9 to the wheel brake 10.
  • a return line 12 or 14 leads from each of the two wheel brakes 8 and 10 to a low-pressure accumulator 15.
  • the return lines 12 and 14 are each provided with an outlet valve 11 and 13, respectively, which are electromagnetically operated, normally closed 2/2 Directional valves are designed.
  • the low-pressure accumulator 15 is connected to the suction side of a return pump 17 via a suction line 16, which will be referred to later as the second suction line connected.
  • the first suction line 18 of the return pump 17 is connected to the brake line 3 between the master cylinder 1 and the isolation valve 4.
  • the first suction line is provided with a changeover valve 19, which is an electromagnetically actuated, normally closed 2/2-way valve.
  • the return pump 17 is connected with its pressure side via a pressure line 20 to the brake line 3 between the separating valve 4 on the one hand and the inlet valves 7 and 9 on the other hand.
  • the return pump 17 is designed to be self-priming, but has a pre-charging device above the master cylinder 1.
  • the connection between the reservoir 22 and the wheel brakes is interrupted by the pressure chambers of the master cylinder 1.
  • the master cylinder pressure on the suction side of the return pump is available when the changeover valve 19 is actuated, so that preloading is not necessary.
  • the brake pedal 21 is not actuated, the connection between the reservoir 22 and the brake line 3 is opened through the master cylinder 1.
  • the master cylinder 1 has two container connections 23 and 24, which are assigned to two master cylinder connections 25 and 26 of the storage container.
  • a switching valve 27 is inserted, a pressure-free, hydraulically operated 2/2-way valve.
  • the connecting line between the switching valve 27 and the follow-up connection 23 is connected to the pressure side of a charge pump 28 via a check valve 31, which has a pre-pressure of approximately 1 bar.
  • the suction side of the charge pump 28 is on the reservoir 22 connected. This arrangement means that the charge pump 28 and the switching valve 27 are connected in parallel.
  • the switching valve 27 is acted upon by the delivery pressure of the charge pump 28 in the closing direction, while the pressure at the follow-up connection 23 acts in the opening direction of the switching valve 27.
  • the pressure at the follow-up connection 23 is always lower than that on the pressure side of the charge pump 28 during active braking with the isolating valve 4 closed, which keeps the brake pressure in the wheel brakes 8 and 10, so that the switching valve is closed in such cases.
  • the effective area in the opening direction is chosen to be smaller than that in the closing direction, as will be explained later with reference to FIG. 2.
  • the delivery pressure of the charge pump 28 passes through the master cylinder 1, the brake line 3 and the first suction line 18 directly to the suction side of the return pump 17.
  • the check valve 4 is connected in a known manner in parallel with a check valve 29, through which the precharge pressure directly into the wheel brakes 8 and 10 arrives, even if the isolating valve is closed for the purpose of automatic braking.
  • the air play of the brakes can be quickly overcome.
  • the pressure in the wheel brakes increases to the precharge pressure. A further pressure build-up can then only take place with the help of the return pump.
  • a pressure limiting valve 30 is arranged parallel to the switching valve 27 and has an opening pressure of approximately 10 bar, at which the pressure side of the charge pump 28 is connected to the reservoir 22.
  • this pressure limiting valve 30 can also be replaced by one parallel to the charge pump.
  • the brake system shown is preloaded via the overrun space of the first brake circuit. The inflow of pressure medium fills the first brake circuit I, but also displaces the intermediate piston of the master cylinder 1. In this way, the second brake circuit II is also charged with the boost pressure.
  • FIG. 2a shows a constructive solution for a hydraulically actuated switching valve 27 according to FIG. 1.
  • the arrangement according to FIG. 2a has two parallel housing bores 41 and 42 in a housing 40.
  • the pressure limiting valve 30 is accommodated in the narrower bore 41, which has a pre-pressure of approximately 10 bar, while the switching valve 27 with an integrated check valve 31 is built into the housing bore 42 of larger diameter.
  • a vertical bore 43 running perpendicular to the two housing bores 41 and 42 connects the two inlets of the check valve 31 and the pressure limiting valve 30 to the pressure side of the charge pump 28.
  • the switching valve 27 has a piston 44, one end face 45 of which is exposed to the delivery pressure of the charge pump 28.
  • the other end of the piston 45 has a step 46, which is biased by a compression spring 47 to the pressure side of the loading pump 28.
  • An extension 48 of smaller diameter carries a sealing ring 49 as a valve closing member, which cooperates with a valve seat 50 designed as a conical taper of the housing bore 42.
  • the end of the extension 48 projects into a narrower section 51 of the bore 42 and has notches 52 on its circumference, which even with axial guidance of the extension 48, a volume flow along this extension is permitted.
  • the piston 44 is axially pierced and accommodates the check valve 31 centrally in its interior, which allows a pressure medium flow from the pressure side of the charge pump 28.
  • a pressure medium outlet 53 is created, which is connected to the wake up port 23.
  • a further connecting bore from the housing bore 42 at the outlet of the pressure relief valve 30 along to the container connection 25 of the storage container 22.
  • the housing bores 41 and 42 are shown to the right in relation to the atmosphere locked up.
  • an elastic sleeve 54 is inserted into the housing bore 41, which is held sealingly in the housing 40 by means of a pressed-in ball 55.
  • the housing bore 42 is closed by means of a cover 56 which is caulked to the housing 40 in a pressure-tight manner.
  • the cover 56 has axial extensions which form a stop for the piston 44 which is fixed to the housing.
  • the arrangement according to FIG. 2a works as follows: the charge pump 28 is switched on during active braking. The delivery pressure moves the piston 44 to the left until the sealing ring 49 comes into contact with the valve seat 50 and the switching valve 27 closes. From a bar overpressure on the part of the charge pump 28, the pressure medium flows via the check valve 31 to the follow-up connection 23 of the master cylinder. If the full delivery volume of the charge pump is not within the brake system recorded, this flows through the pressure regression valve 30 from 10 bar overpressure into the storage container 22. At the end of active braking, the return pump 17 feeds the pressure medium volume of the brake circuit I back into the master cylinder 1.

Landscapes

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

Abstract

Pour amorcer les pompes de refoulement (17) à amorçage automatique d'un système de freinage à régulation antipatinage, par exemple à de basses températures, il est prévu une pompe d'amorçage (28) entre le réservoir (22) et le maître-cylindre (1), qui refoule du fluide hydraulique dans un raccordement de chasse (23) du maître-cylindre (1) par l'intermédiaire d'un clapet antiretour. Ledit fluide hydraulique parvient côté aspiration des pompes de refoulement (17) par inversion d'une soupape de commutation (4) électromagnétique. Pour un freinage normal, il est prévu une connexion entre le réservoir (22) et le maître-cylindre (1), pourvue d'une soupape de commande (27). Cette soupape de commande (27) est fermée afin de permettre l'amorçage de la pompe de refoulement (17). Cette soupape de commande (27) se présente sous forme de soupape à commande hydraulique, sollicitée en position fermée par la pression de refoulement de la pompe d'amorçage (28) et en position ouverte, par la pression régnant au niveau du raccordement de chasse (23).
PCT/EP1997/000285 1996-02-03 1997-01-22 Systeme de freinage hydraulique a regulation antipatinage comportant une pompe d'amorçage WO1997028031A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP9527275A JP2000503933A (ja) 1996-02-03 1997-01-22 充填ポンプを備えたスリップコントロール式液圧ブレーキ装置
EP97901582A EP0874748A1 (fr) 1996-02-03 1997-01-22 Systeme de freinage hydraulique a regulation antipatinage comportant une pompe d'amorcage

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19603871.5 1996-02-03
DE1996103871 DE19603871A1 (de) 1996-02-03 1996-02-03 Schlupfgeregelte hydraulische Bremsanlage mit Ladepumpe

Publications (1)

Publication Number Publication Date
WO1997028031A1 true WO1997028031A1 (fr) 1997-08-07

Family

ID=7784404

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1997/000285 WO1997028031A1 (fr) 1996-02-03 1997-01-22 Systeme de freinage hydraulique a regulation antipatinage comportant une pompe d'amorçage

Country Status (4)

Country Link
EP (1) EP0874748A1 (fr)
JP (1) JP2000503933A (fr)
DE (1) DE19603871A1 (fr)
WO (1) WO1997028031A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997042067A1 (fr) * 1996-05-08 1997-11-13 Robert Bosch Gmbh Systeme de freinage hydraulique pour vehicule
GB2350654A (en) * 1999-06-02 2000-12-06 Rover Group A brake modulation arrangement
US6431662B2 (en) 2000-03-01 2002-08-13 Toyota Jidosha Kabushiki Kaisha Vehicle braking pressure source device wherein fluid communication between pressurizing and back-pressure chambers of master cylinder is controlled based on vehicle running state and/or road surface condition
IT202200007445A1 (it) * 2022-04-14 2023-10-14 Brembo Spa Serbatoio per fluido frenante

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3337545A1 (de) * 1983-10-15 1985-04-25 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische bremsanlage
DE3900852C1 (de) * 1989-01-13 1990-03-01 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart Antriebs-Schlupf-Regeleinrichtung (ASR) an einem auch mit einem Antiblockiersystem ausgerüsteten Straßenfahrzeug
DE3900850C1 (fr) * 1989-01-13 1990-03-22 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De
EP0460408A1 (fr) * 1990-06-02 1991-12-11 Robert Bosch Gmbh Installation hydraulique de freinage pour véhicule avec système anti-blocage et contrôle de traction
WO1992017357A1 (fr) * 1991-04-04 1992-10-15 Alfred Teves Gmbh Dispositif de freinage de vehicules a moteur a regulation de la pression de freinage en fonction du patinage au freinage et a l'entrainement
DE4128091A1 (de) * 1991-08-24 1993-02-25 Teves Gmbh Alfred Bremsanlage mit blockierschutz-und antriebsschlupfregelung
DE4232311C1 (de) * 1992-09-26 1994-02-24 Bosch Gmbh Robert Hydraulische Fahrzeugbremsanlage mit Blockierschutzeinrichtung
DE4329139C1 (de) * 1993-08-30 1994-07-28 Daimler Benz Ag Bremsdruck-Steuereinrichtung
WO1997002166A1 (fr) * 1995-07-05 1997-01-23 Itt Automotive Europe Gmbh Systeme de freinage hydraulique a regulation antipatinage comportant une pompe de suralimentation

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3832722A1 (de) * 1988-09-27 1990-03-29 Bosch Gmbh Robert Bremsanlage
JP2980920B2 (ja) * 1989-08-03 1999-11-22 日本エービーエス株式会社 車両用液圧ブレーキ制御装置
DE4037468A1 (de) * 1990-11-24 1992-05-27 Daimler Benz Ag Verfahren zur aktivierung der hydraulischen betriebsbremsanlage eines strassenfahrzeuges
DE4309470C2 (de) * 1993-03-24 2002-09-19 Bosch Gmbh Robert Hydraulische Fahrzeugbremsanlage mit Blockierschutzeinrichtung

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3337545A1 (de) * 1983-10-15 1985-04-25 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische bremsanlage
DE3900852C1 (de) * 1989-01-13 1990-03-01 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart Antriebs-Schlupf-Regeleinrichtung (ASR) an einem auch mit einem Antiblockiersystem ausgerüsteten Straßenfahrzeug
DE3900850C1 (fr) * 1989-01-13 1990-03-22 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De
EP0460408A1 (fr) * 1990-06-02 1991-12-11 Robert Bosch Gmbh Installation hydraulique de freinage pour véhicule avec système anti-blocage et contrôle de traction
WO1992017357A1 (fr) * 1991-04-04 1992-10-15 Alfred Teves Gmbh Dispositif de freinage de vehicules a moteur a regulation de la pression de freinage en fonction du patinage au freinage et a l'entrainement
DE4128091A1 (de) * 1991-08-24 1993-02-25 Teves Gmbh Alfred Bremsanlage mit blockierschutz-und antriebsschlupfregelung
DE4232311C1 (de) * 1992-09-26 1994-02-24 Bosch Gmbh Robert Hydraulische Fahrzeugbremsanlage mit Blockierschutzeinrichtung
DE4329139C1 (de) * 1993-08-30 1994-07-28 Daimler Benz Ag Bremsdruck-Steuereinrichtung
WO1997002166A1 (fr) * 1995-07-05 1997-01-23 Itt Automotive Europe Gmbh Systeme de freinage hydraulique a regulation antipatinage comportant une pompe de suralimentation

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997042067A1 (fr) * 1996-05-08 1997-11-13 Robert Bosch Gmbh Systeme de freinage hydraulique pour vehicule
GB2350654A (en) * 1999-06-02 2000-12-06 Rover Group A brake modulation arrangement
US6431662B2 (en) 2000-03-01 2002-08-13 Toyota Jidosha Kabushiki Kaisha Vehicle braking pressure source device wherein fluid communication between pressurizing and back-pressure chambers of master cylinder is controlled based on vehicle running state and/or road surface condition
IT202200007445A1 (it) * 2022-04-14 2023-10-14 Brembo Spa Serbatoio per fluido frenante
WO2023199278A1 (fr) * 2022-04-14 2023-10-19 Brembo S.P.A. Réservoir de liquide de frein

Also Published As

Publication number Publication date
JP2000503933A (ja) 2000-04-04
DE19603871A1 (de) 1997-08-07
EP0874748A1 (fr) 1998-11-04

Similar Documents

Publication Publication Date Title
EP0621837B1 (fr) Dispositif de regulation de la pression des freins, utile notamment pour reguler le patinage a l'acceleration des roues motrices
DE3627000C2 (de) Bremsanlage mit Schlupfregelung
DE3607367C2 (de) Hydraulische Bremsanlage für Kraftfahrzeuge
EP0504334B1 (fr) Systeme de freinage avec installation servant a la fois pour la regulation du glissement au freinage et pour la regulation du glissement a l'entrainement
DE2450874C3 (de) Blockiergeschützte hydraulische Fahrzeugbremsanlage
EP0930208B1 (fr) Système hydraulique de freinage pou véhicules à moteur
DE3827366A1 (de) Blockiergeschuetzte hydraulische bremsanlage
DE69008788T2 (de) Bremsflüssigkeitsspender für Blockierschutzbremssysteme.
DE4110851A1 (de) Kraftfahrzeugbremsanlage mit bremsschlupf- und antriebsschlupfabhaengiger regelung des bremsdruckes
DE4000837A1 (de) Hydraulische bremsanlage mit einer einrichtung zur brems- und/oder antriebsschlupfregelung
DE4415651C1 (de) Bremsdruck-Steuereinrichtung
DE2430167A1 (de) Stufenhauptzylinder mit einem fuellkolben
DE2725941A1 (de) Bremsvorrichtung
WO1997002166A1 (fr) Systeme de freinage hydraulique a regulation antipatinage comportant une pompe de suralimentation
DE19626289B4 (de) Hydraulische Bremsanlage mit einer Rückförderpumpe
EP0494272B1 (fr) Systeme hydraulique de freinage a anti-derapeur automatique
DE3734903A1 (de) Hydraulische bremsanlage fuer kraftfahrzeuge mit abs
DE4021454A1 (de) Hydraulische bremsanlage
EP0874748A1 (fr) Systeme de freinage hydraulique a regulation antipatinage comportant une pompe d'amorcage
EP0625106B1 (fr) Systeme de freinage antipatinage
DE2703760A1 (de) Zweikreis-bremsanlage
DE3819812A1 (de) Blockierschutzregelanlage
DE2609904A1 (de) Hydraulischer bremsverstaerker
DE4023708A1 (de) Blockiergeschuetzte, hydraulische bremsanlage
DE4024627A1 (de) Hydraulische fahrzeugbremsanlage mit blockierschutz- und antriebsschlupfbegrenzungseinrichtung

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): JP US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LU MC NL PT SE

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 1997901582

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: CA

WWP Wipo information: published in national office

Ref document number: 1997901582

Country of ref document: EP

WWR Wipo information: refused in national office

Ref document number: 1997901582

Country of ref document: EP

WWW Wipo information: withdrawn in national office

Ref document number: 1997901582

Country of ref document: EP

点击 这是indexloc提供的php浏览器服务，不要输入任何密码和下载