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WO1996004160A1 - Systeme de freinage hydraulique a regulation antipatinage - Google Patents

Systeme de freinage hydraulique a regulation antipatinage Download PDF

Info

Publication number
WO1996004160A1
WO1996004160A1 PCT/EP1995/002947 EP9502947W WO9604160A1 WO 1996004160 A1 WO1996004160 A1 WO 1996004160A1 EP 9502947 W EP9502947 W EP 9502947W WO 9604160 A1 WO9604160 A1 WO 9604160A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
brake
wheel brake
hydraulic
valve
Prior art date
Application number
PCT/EP1995/002947
Other languages
German (de)
English (en)
Inventor
Dalibor Zaviska
Paul Linhoff
Original Assignee
Itt Automotive Europe 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
Application filed by Itt Automotive Europe Gmbh filed Critical Itt Automotive Europe Gmbh
Publication of WO1996004160A1 publication Critical patent/WO1996004160A1/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
    • B60T8/36—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
    • B60T8/3655—Continuously controlled electromagnetic valves
    • B60T8/366—Valve details
    • B60T8/367—Seat valves, e.g. poppet valves
    • 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
    • B60T8/364—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems switching between a number of discrete positions as a function of the applied signal, e.g. 3/3-valves
    • 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
    • B60T8/3655—Continuously controlled electromagnetic valves
    • B60T8/366—Valve details
    • B60T8/3665—Sliding valves
    • 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

Definitions

  • the invention relates to a hydraulic brake system with wheel slip control according to the preamble of the claim
  • the invention has therefore set itself the task of improving a brake system of the aforementioned type in such a way that a functionally reliable and low-noise pressure medium control is ensured with the least possible construction effort.
  • the pressure modulation valve is designed as a 4/3-way valve, which connects the brake pressure transmitter to the wheel brake in the basic position, and the pressure medium supply from the brake pressure transmitter to the wheel brake in the other switching positions either throttles or blocks and / or connects the wheel brake to the return line.
  • the throttling of the pressure medium supply to the wheel brake takes place by means of a flow control valve, whereby a constant volume flow with constant control properties is set independently of operating pressure fluctuations.
  • the features of claim 3 include the individual adjustment of the switching pressure for the flow control valve as a function of the pressure difference between the brake pressure transmitter and the wheel brake in order to bring about a throttled pressure medium supply to the wheel brake. Different pressure build-up gradients can thus be represented in brake operation. For the throttled pressure medium supply to the wheel brake to take effect, it is to be taken as a basis that the changeover pressure is generally lower than the differential pressure between the brake pressure sensor and the wheel brake.
  • the switching of the pressure modulation valve takes place by a current-proportional excitation of an electromagnet, in which the pressure medium supply from the brake pressure transmitter to the wheel brake is blocked.
  • the flow-proportional control of the pressure modulation valve ensures the exact setting of the pressure medium connections to be separated or connected in each case during the pressure maintenance and pressure reduction phase of a wheel slip-controlled braking.
  • claim 5 provides that the switching position of the pressure modulation valve assigned to the pressure medium supply from the wheel brake to the return line is ensured by the current-proportional excitation of an electromagnet.
  • a suitable construction for accommodating the flow control valve in the pressure modulation valve by means of a valve carrier is evident from claim 6.
  • the flow control valve as a piston in a stepped bore of the valve carrier, which is provided with a pressure pin to relieve the pressure on the wheel brakes in the direction of the return line.
  • claim 8 proposes to arrange an actuating member on the piston side facing away from the pressure pin, said actuating element being controllable by the proportional magnet.
  • the pressure relief of the wheel brake during a wheel slip control takes place according to the features of claim 9 by means of a check valve cooperating with the pressure pin, which in its basic position blocks the pressure medium connection between the wheel brake and the return line.
  • the basic setting of the piston advantageously takes over a compression spring, the actuating force of which is greater than the force of a spring that positions the proportional magnet.
  • through-bores are arranged on the circumference of the piston for the control of the pressure medium connection between the brake pressure transmitter and the wheel brake, which release transverse channels arranged in the valve carrier in the basic position of the piston.
  • At least one measuring orifice is expediently arranged within the end face of the piston, which has the pressure pin, so that this feature relating to claim 12, in view of the preceding features for the arrangement of the through bores in the piston of the current regulator, the desired pressure build-up gradient was determined during wheel slip control.
  • a pressure difference is generated at the measuring orifice, which moves the piston against the compression spring to control the volume flow of the pressure medium flowing from the master cylinder to the wheel brake.
  • the maximum control cross section of the through hole which is assigned to the cross channel leading to the wheel brake, is chosen to be smaller than the maximum control cross section of the through hole, which is assigned to the cross channel leading to the brake pressure sensor, so that the through bore in the piston corresponding to the wheel brake connection initially remains blocked during a pressure build-up phase. Due to the pressure difference at the orifice plate, the through hole cooperating with the brake pressure sensor connection then takes over the current control function.
  • FIG. 1 shows a hydraulic circuit diagram for a brake system with slip control according to the invention
  • Figure 2 is a sectional view through the pressure modulation valve according to the invention.
  • FIG. 1 schematically shows the hydraulic circuit structure of the brake system, according to which the brake pressure transmitter 2 is connected to the wheel brake 3 via the pressure modulation valve 1 which is open in the basic position.
  • the pressure modulation valve is designed as a 3/4-way valve, so that, according to the illustration, the pressure-free return line 4 from the line connecting the brake pressure sensor 2 to the wheel brake 3 path is separated.
  • the return line 4 connects to the suction side of a pump 17, there being a connection to an unpressurized storage reservoir 16.
  • the pressure side of the pump 17 opens into the main pressure line 18.
  • the valve switching position shown in the illustration corresponds to the brake release, normal brake and pressure build-up position when the wheel slip control is inactive.
  • the pressure modulation valve switches to the position in which all three pressure medium connections are separated from one another. This as well as the subsequent pressure reduction position of the pressure modulation valve 1 in the wheel slip control phase are controlled by the proportional magnet of the pressure modulation valve 1. In the pressure reduction position of the pressure modulation valve 1 there is then an unimpeded pressure medium connection between the wheel brake 3 and the return line 4 while the brake pressure transmitter 2 remains separated from the connection of the wheel brake 3. A renewed pressure build-up in the wheel brake takes place without excitation of the proportional magnet, in which a pressure spring 11 of the pressure modulation valve 1 shifts the latter into its volume flow control function.
  • FIG. 2 shows in cross section the pressure modulation valve 1, which has a valve carrier 5 in which the piston 7 of the flow control valve is displaceably guided in a stepped bore 8.
  • the proportional magnet essentially consists of a magnet armature, to which a magnetic core is assigned, a pressure spring 12 being clamped between the aforementioned two parts, which surrounds the actuating element 9 which extends into the stepped bore 8.
  • the actuator 9 is part of the magnet armature and is supported on an end face of the piston 7.
  • a push pin 6 is located on the opposite end face of the piston 7 attached, facing a check valve 10 closed in the basic position. All previously described details of the pressure modulation valve 1 are in a coaxial arrangement with one another.
  • the piston 7 of the flow control valve is pressed against the actuator 9 in the basic position shown by the action of a compression spring 11.
  • the compression spring 11 is clamped between the end face of the piston 7 having the pressure pin 6 and a valve seat body of the check valve 10.
  • the piston 7 has a plurality of measuring orifices 15 in the area of its end face which has the pressure pin 6, while the jacket surface of the piston 7 is provided with through-bores 13 which are widened in sections to form control edges and are spaced apart from one another which correspond to the transverse channels 14 arranged in the valve carrier 5.
  • the transverse channel 14 located in the upper region of the valve carrier 5 is connected to the brake pressure transmitter 2, while the pressure medium connection to the wheel brake 3 is established via two transverse channels 14 running parallel in the lower region of the valve carrier 5.
  • the two transverse channels 14 assigned to the wheel brake 3 are spaced apart from one another in such a way that in the basic position of the pressure modulation valve a pressure medium connection is established both via the transverse bore 13 arranged in the lower region of the piston 7 and through the measuring orifice 15.
  • the pressure medium connection is to be flowed through in each case via ring filter elements on the valve support 5, a bypass connection from the wheel brake 3 in the direction of the brake pressure transmitter 2 being present in the area of a non-return sleeve 19 attached to the valve support 5.
  • the position of the pressure modulation valve shown in the illustration corresponds to the operating release as well as the normal braking position, in which wheel slip control is excluded.
  • the Piston 7 with its through bores 13 is in a position into which pressure medium reaches the wheel brake 3 unhindered from the brake pressure transmitter 2 via the transverse channels 13 and the measuring orifices 15.
  • the amount of pressure spring 11 acting on the piston 7 is greater than the force generated by the pressure drop at the orifice plates 15. The piston 7 thus remains in the position shown in the illustration.
  • the proportional magnet is energized, so that the actuating member 9 displaces the piston 7 against the action of the compression springs 11, 12 until the actuating member 9 has approached the check valve 10 with its push pin 6 .
  • the transverse channels 14 leading to the wheel brake 3 are initially closed by the piston edge, so that only a throttled volume flow can flow in through the orifice plates 15 to the wheel brake 3 for a short time, until afterwards also the upper through duct gear bore 13 in the piston 7, the throttle bore in the transverse channel 14 of the pressure medium path connected to the brake pressure sensor 2 is blocked by the piston edge.
  • An interruption of the brake actuation during the pressure maintenance phase then leads to a pressure relief of the non-return sleeve 19 blocking in the direction of the wheel brake 3, so that the pressure medium volume clamped in the wheel brake 3 is relieved via the non-return sleeve 19 in the direction of the brake pressure transmitter 2 can.
  • the pressure reduction phase during the wheel slip control takes place by appropriate current control of the proportional solenoid in such a way that the pressure pin 6 opens the check valve 10, so that the pressure medium volume clamped in the wheel brake 3 during brake operation flows in the direction of the pressure-free return line 4.
  • the current Supply to the proportional magnet is interrupted, as a result of which the compression spring 12 ensures a return movement of the actuating member 9, the compression spring 11 acting on the piston 7 also moving the flow control valve into a position in which a connection of the throttle bore in the transverse channel 14 of the brake pressure sensor 2 via the orifice plates 15 to the transverse channel 14 of the wheel brake 3. Accordingly, the throttle bore is only gradually released from the piston edge, while the transverse channels 14 assigned to the wheel brake 3 initially remain blocked by the small cutout in the through bore 13.
  • the proposed design enables the flow control valve to be actuated in such a way that the optimal pressure build-up gradient can be set during ABS control with a corresponding volume absorption of the wheel brake in the case of non-excited proportional magnets. Smaller pressure build-up gradients in brake pressure control are also possible through the use of a proportional magnet. This creates a brake system that enables comfortable control of the wheel cylinder pressure with different pressure build-up radii and minimal space requirements.

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 hydraulique à régulation antipatinage, qui comprend un générateur de pression de freinage (2) relié hydrauliquement à au moins un frein de roue (3), par l'intermédiaire d'une conduite de hydraulique principale (18), une conduite de retour (4) raccordée au frein de roue, qui est reliée à un réservoir d'alimentation (16), une pompe (17) qui comprend une conduite hydraulique en liaison hydraulique avec la conduite hydraulique principale (18), au moins une soupape de modulation de pression (1) qui maintient ouvert ou fermé le passage du fluide hydraulique dans la conduite principale (18) ainsi que dans la conduite de retour (4). La soupape de modulation de pression (1) se présente sous forme de vanne 3/4 voies qui en position initiale, relie le générateur de pression de freinage (2) au frein de roue (3), et dans les autres positions de commutation, réduit ou ferme l'alimentation en fluide hydraulique allant du générateur de pression de freinage (2) au frein de roue (3) et/ou relie le frein de roue (3) à la conduite de retour (4).
PCT/EP1995/002947 1994-08-05 1995-07-26 Systeme de freinage hydraulique a regulation antipatinage WO1996004160A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4427800.4 1994-08-05
DE19944427800 DE4427800A1 (de) 1994-08-05 1994-08-05 Hydraulische Bremsanlage mit Radschlupfregelung

Publications (1)

Publication Number Publication Date
WO1996004160A1 true WO1996004160A1 (fr) 1996-02-15

Family

ID=6525029

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1995/002947 WO1996004160A1 (fr) 1994-08-05 1995-07-26 Systeme de freinage hydraulique a regulation antipatinage

Country Status (2)

Country Link
DE (1) DE4427800A1 (fr)
WO (1) WO1996004160A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001062566A1 (fr) * 2000-02-25 2001-08-30 Continental Teves Ag & Co. Ohg Electrovanne

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59601425D1 (de) * 1995-05-18 1999-04-15 Lucas Ind Plc Elektromagnetische ventilanordnung und fahrzeugbremssystem mit dieser elektromagnetischen ventilanordnung
DE19635589B4 (de) * 1996-09-02 2006-09-21 Lucas Industries Plc, Solihull Hydraulische Bremsanlage für ein Landfahrzeug
DE19711442A1 (de) * 1997-03-19 1998-09-24 Itt Mfg Enterprises Inc Einlaßventil mit integrierter Blende
DE19727654B4 (de) * 1997-06-30 2005-11-24 Continental Teves Ag & Co. Ohg Hydraulisches Ventil

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2230883A1 (fr) * 1973-05-24 1974-12-20 Ferodo Sa
FR2311697A1 (fr) * 1975-05-23 1976-12-17 Ferodo Sa Dispositif de modulation, notamment pour circuit de freinage de vehicule automobile et circuit de freinage equipe d'un tel dispositif
FR2451528A2 (fr) * 1978-05-20 1980-10-10 Bosch Gmbh Robert Electrovalve
DE3402794A1 (de) * 1983-03-03 1984-09-06 Robert Bosch Gmbh, 7000 Stuttgart Antiblockierregelsystem
DE3607693A1 (de) * 1986-03-08 1987-09-10 Bosch Gmbh Robert Ventilanordnung
EP0369412A2 (fr) * 1988-11-14 1990-05-23 Sumitomo Electric Industries, Ltd. Appareil de commande de pression de fluide
JPH03132454A (ja) * 1989-10-19 1991-06-05 Nissan Motor Co Ltd アンチスキッド用制御弁
EP0452173A1 (fr) * 1990-04-12 1991-10-16 Alliedsignal Europe Services Techniques Système de régulation de pression à commande électrique pour un circuit hydraulique
WO1992016397A1 (fr) * 1991-03-13 1992-10-01 Alfred Teves Gmbh Groupe hydraulique pour dispositifs de commande ou de regulation hydrauliques
WO1992018362A1 (fr) * 1991-04-19 1992-10-29 Alfred Teves Gmbh Electrovanne, en particulier pour systemes de freinage antipatinage pour vehicules automobiles
WO1993008051A1 (fr) * 1991-10-25 1993-04-29 Itt Automotive Europe Gmbh Vanne electromagnetique a bruit reduit, notamment pour systeme hydrauliques de freinage a systeme d'antipatinage a l'acceleration
US5248191A (en) * 1990-03-27 1993-09-28 Nippondenso Co., Ltd. Pressure control valve for continuous pressure control to wheel cylinder

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3124755A1 (de) * 1981-06-24 1983-01-13 Robert Bosch Gmbh, 7000 Stuttgart Fahrzeugbremsanlage
DE3739915C2 (de) * 1987-11-25 1995-07-13 Teves Gmbh Alfred Hydraulische Bremsanlage mit einer Antriebsschlupfregelung
AU610722B2 (en) * 1988-05-31 1991-05-23 Sumitomo Electric Industries, Ltd. Antilock mechanism
JP2853237B2 (ja) * 1990-02-09 1999-02-03 住友電気工業株式会社 液圧制御装置
DE4034839C1 (fr) * 1990-11-02 1992-03-19 Manfred 2300 Kiel De Schlaupitz
FR2669883B1 (fr) * 1990-11-29 1993-01-29 Bendix Europ Services Tech Dispositif de freinage automatique pour vehicule.
DE4041506C2 (de) * 1990-12-22 1995-01-19 Bosch Gmbh Robert Absperrventil in einer hydraulischen Bremsanlage, insbesondere für Kraftfahrzeuge
DE4134490A1 (de) * 1991-10-18 1993-04-22 Teves Gmbh Alfred Blockiergeschuetzte hydraulische bremsanlage
DE4237561C2 (de) * 1991-11-07 1998-06-04 Tokico Ltd Antiblockiersystem
DE4213710A1 (de) * 1992-04-25 1993-10-28 Bosch Gmbh Robert Blockierschutz- und Antriebsschlupf-Regelsystem

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2230883A1 (fr) * 1973-05-24 1974-12-20 Ferodo Sa
FR2311697A1 (fr) * 1975-05-23 1976-12-17 Ferodo Sa Dispositif de modulation, notamment pour circuit de freinage de vehicule automobile et circuit de freinage equipe d'un tel dispositif
FR2451528A2 (fr) * 1978-05-20 1980-10-10 Bosch Gmbh Robert Electrovalve
DE3402794A1 (de) * 1983-03-03 1984-09-06 Robert Bosch Gmbh, 7000 Stuttgart Antiblockierregelsystem
DE3607693A1 (de) * 1986-03-08 1987-09-10 Bosch Gmbh Robert Ventilanordnung
EP0369412A2 (fr) * 1988-11-14 1990-05-23 Sumitomo Electric Industries, Ltd. Appareil de commande de pression de fluide
JPH03132454A (ja) * 1989-10-19 1991-06-05 Nissan Motor Co Ltd アンチスキッド用制御弁
US5248191A (en) * 1990-03-27 1993-09-28 Nippondenso Co., Ltd. Pressure control valve for continuous pressure control to wheel cylinder
EP0452173A1 (fr) * 1990-04-12 1991-10-16 Alliedsignal Europe Services Techniques Système de régulation de pression à commande électrique pour un circuit hydraulique
WO1992016397A1 (fr) * 1991-03-13 1992-10-01 Alfred Teves Gmbh Groupe hydraulique pour dispositifs de commande ou de regulation hydrauliques
WO1992018362A1 (fr) * 1991-04-19 1992-10-29 Alfred Teves Gmbh Electrovanne, en particulier pour systemes de freinage antipatinage pour vehicules automobiles
WO1993008051A1 (fr) * 1991-10-25 1993-04-29 Itt Automotive Europe Gmbh Vanne electromagnetique a bruit reduit, notamment pour systeme hydrauliques de freinage a systeme d'antipatinage a l'acceleration

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 15, no. 339 (M - 1152)<4867> 28 August 1991 (1991-08-28) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001062566A1 (fr) * 2000-02-25 2001-08-30 Continental Teves Ag & Co. Ohg Electrovanne

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Publication number Publication date
DE4427800A1 (de) 1996-02-08

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