EP0720549A1 - Vanne electromagnetique, notamment pour systemes de freinage hydrauliques antipatinage pour automobiles - Google Patents

Vanne electromagnetique, notamment pour systemes de freinage hydrauliques antipatinage pour automobiles

Info

Publication number
EP0720549A1
EP0720549A1 EP94926102A EP94926102A EP0720549A1 EP 0720549 A1 EP0720549 A1 EP 0720549A1 EP 94926102 A EP94926102 A EP 94926102A EP 94926102 A EP94926102 A EP 94926102A EP 0720549 A1 EP0720549 A1 EP 0720549A1
Authority
EP
European Patent Office
Prior art keywords
valve
seat
pressure medium
closing member
chamber
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.)
Withdrawn
Application number
EP94926102A
Other languages
German (de)
English (en)
Inventor
Klaus Mueller
Bernhard Heugle
Kurt Herzog
Martin Oehler
Günther HOHL
Hans-Jürgen HERDERICH
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0720549A1 publication Critical patent/EP0720549A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/20—Control of fluid pressure characterised by the use of electric means
    • G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
    • G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
    • G05D16/2022—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means actuated by a proportional solenoid
    • 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

Definitions

  • Electromagnetically actuated valve in particular for slip-controlled hydraulic brake systems in motor vehicles
  • the invention is based on an electromagnetically actuated valve, in particular for slip-controlled hydraulic brake systems in motor vehicles, according to the preamble of the main claim.
  • Such a valve is known from DE 39 34 771 Cl, Figure 3. It has a control piston which is arranged in the valve dome and forms a stop for the magnet armature and which is guided in a longitudinally displaceable manner on a pin which extends from the valve body and penetrates the magnet armature.
  • the control piston with its base facing away from the anchor, delimits a control chamber which is connected to the pressure medium inlet of the known valve by a pressure medium channel penetrating the pin and the control piston at the same axis. While the magnet armature is pressure-balanced on both end faces, pressure introduced into the control chamber is able to axially shift the control piston against a stop.
  • This mode of operation of the known valve can be used in slip-controlled hydraulic brake systems in which the pressure medium inlet is connected to the master brake cylinder and the pressure medium outlet is connected to a wheel brake cylinder.
  • the valve is switched into its closed position by energizing the magnet coil and, when the pressure in the wheel brake cylinder is reduced, a pressure gradient of sufficient height is generated between the pressure medium inlet and the pressure medium outlet, this results in the above-described displacement of the control piston that the mentioned throttling of the flow cross-section takes effect when the valve is opened, as long as the pressure difference between the inlet and outlet exists.
  • the reduction in the flow rate cut has a favorable effect on the control quality and the noise behavior of the brake system due to the reduced pressure gradient in the pressure build-up of a brake slip control following a pressure reduction. With normal braking without risk of blocking, however, the full flow cross-section of the valve is available, which promotes a desired short response time of the brake system when the brake is applied.
  • the fixed setting of the throttled flow cross section is disadvantageous because the flow rate is subject to fluctuations dependent on the differential pressure.
  • the flow rate is very much dependent on the absolute measure of the flow cross section, i.e. the stop requires a very narrow tolerance.
  • the valve is relatively expensive due to the control piston required.
  • the valve according to the invention with the characterizing features of the main claim has the advantage that the flow section of the first seat valve changes when the second one is open Depending on the forces acting on the armature, but without magnetic force, the seat valve automatically adjusts to largely constant flow rates, which are lower than the full opening of the first seat valve, given a sufficiently large pressure drop between the inlet and outlet sides of the valve.
  • the structural effort to achieve this function of the valve according to the invention as a flow control valve is extremely low.
  • the design of the second seat valve with only one movable component which interacts with the valve seat is particularly advantageous with regard to costs and functional reliability.
  • Another advantage is the sealed guidance of the magnet armature in the valve dome, because this creates a pressure separation of the two armature faces for the generation of a force effect on the magnet armature in a simple manner.
  • the guidance of the pressure medium jet into the space delimited by the guide body is distinguished in an advantageous manner because the dynamic pressure generated thereby increases the pressure drop acting on the magnet armature.
  • FIG. 1 shows a longitudinal section through an electromagnetically actuated valve
  • FIGS. 2 and 3 variants the detail marked X in FIG. 1 in the area of a seat valve, on a different scale.
  • An electromagnetically actuated valve 10 has a valve housing 11 which is intended to be received in a valve block (not shown) and which is fixedly connected to a yoke disk 12 (FIG. 1).
  • the valve housing 11 is continued beyond the yoke plate 12 with a pole core 13.
  • a tubular valve dome 14 is attached to the pole core 13. It is tightly connected to the pole core 13 by welding.
  • the valve dome 14 facing away from the pole core has a hemispherical end.
  • the valve dome 14 is encompassed by an annular magnetic coil 17.
  • a bell-shaped housing 18 surrounds the magnetic coil 17. The housing 18 engages on the one hand on the valve dome 14; on the other hand, it is connected to the yoke disk 12.
  • valve dome 14 which is closed on the coil side, an essentially circular cylindrical magnet armature 21 is accommodated in a longitudinally movable manner.
  • the valve tappet 22 is received with play in a longitudinal bore 23 of the valve housing 11.
  • the valve tappet 22 carries a spherical closing member 24.
  • the closing member 24, which is designed as a solid ball in the exemplary embodiment, is integrally connected to the valve tappet 22.
  • the closing member 24, facing away from the anchor can also have the shape of a hemisphere or a cone or truncated ball.
  • a sleeve-shaped valve body 27 with a stepped bore 28, which opens into a valve seat 29, is pressed into the section of the longitudinal bore 23 facing away from the anchor.
  • the valve seat 29 is designed as a conical countersink with a cone angle of preferably 90 °.
  • the closing member 24 and the valve seat 29 form a first seat valve 30 of the electromagnetically actuated valve 10.
  • the solenoid 17 When the solenoid 17 is not energized, the first seat valve 30 takes its open position due to the action of a prestressed return spring 31 acting on the valve tappet 22 and on the valve body 27 as a rest position.
  • the valve housing 11 is provided with a transverse bore 34 crossing the longitudinal bore 23 at right angles.
  • a valve chamber 35 accommodating the first seat valve 30 is created in the penetration area of both bores 23 and 34.
  • the valve chamber 35 is connected on the one hand via the valve seat 29 and the stepped bore 28 to a pressure medium inlet; on the other hand, a pressure medium outlet formed by the transverse bore 34 is connected to the valve chamber.
  • valve chamber 35 also contains a guide body 38 for pressure medium (FIG. 2).
  • the guide body 38 is sleeve-shaped and fastened to the valve tappet 22 so as to run parallel to it.
  • the guide body 38 engages around the closing member 24 of the first seat valve 30 to form a radial gap 39 and extends to form an axial gap 40 up to close to the valve body 27, as can be clearly seen in FIG.
  • the axial gap 40 has a larger dimension than the valve lift, ie in the closed position of the first seat valve 30 forming the working position of the valve 10, in which the closing element 24 engages the valve seat 29, the axial gap 40 is open Minimum size reduced.
  • the guide body 38 separates a partial chamber 43 from the valve chamber 35.
  • This valve sub-chamber 43 is connected by a transverse slot 44 of the valve tappet 22 facing away from the valve seat to a first pressure medium channel 45 designed as a continuous longitudinal bore in the valve tappet and in the magnet armature 21.
  • the first pressure medium channel 45 leads to a control chamber 46 which is located between the end face 47 of the magnet armature 21 and the hemispherical end of the valve dome 14.
  • Outside of the guide body 38 also starts from the Ventilka mer 35 from a flattening of the otherwise circular cross-section valve tappet 22 formed, second pressure medium channel 48. This ends at the end face 49 of the magnet armature 21 near the closing member, which lies opposite the pole core 13 while forming a gap.
  • the mouth of the first pressure medium channel 45 facing the control chamber 46 has a conical countersink as a valve seat 52 for a spherical closing body 53 of a second seat valve 54 received in the control chamber 46. This is intended for switching the passage of the first pressure medium channel 45.
  • the second seat valve 54 assumes its closed position, in which the closing body 53 is supported on the one hand on the valve seat 52 and on the other hand on the valve dome 14. In the open position of the second seat valve 54, however, the closing body 53 is loosely received in the countersink of the valve seat 52 and the first pressure medium channel 45 is continuous.
  • the second seat valve 54 can also be provided with a flat seal as a closure means or with a sealing ring partially embedded in the mouth of the magnet armature 21, which in cooperation with the Valve dome 14 controls the passage of the first pressure medium channel 45.
  • Circumferential, i.e. The magnet armature 21 is sealed against the valve dome 14 between the two end faces 47 and 49.
  • This sealing can take place by means of a gap or labyrinth seal; however, it can also consist in the arrangement of a sealing ring 57 or slide ring on the magnet armature 21, as is indicated by dashed lines in FIG. 1.
  • the valve 10 is particularly intended for use in slip-controlled hydraulic brake systems of motor vehicles. It must be arranged in accordance with the brake system shown in FIG. 1 of DE-39 34 771 C1 mentioned at the beginning as an inlet valve in a brake line between a master brake cylinder and a wheel brake cylinder. The pressure medium inlet formed by the stepped bore 28 is then connected to the master brake cylinder, and the transverse bore 34 is connected to the wheel brake cylinder as a pressure medium outlet.
  • the valve 10 can be bypassed by a return line, which starts from the brake line on the side of the wheel brake cylinder and re-opens into the brake line on the side of the master brake cylinder.
  • the main elements in the return line are an outlet valve and a return pump following this in the direction of flow.
  • a check valve 58 is expediently arranged parallel to the valve 10 for bridging the first seat valve 30 between the pressure medium outlet and the pressure medium inlet, which enables an unthrottled backflow from the wheel brake cylinder to the master brake cylinder when the master brake cylinder is depressurized.
  • valve 10 In the event of braking initiated by the driver of the vehicle without the risk of locking, the valve 10 assumes its drawn rest position, ie the first seat valve 30 is open, but the second seat valve 54 is closed.
  • the pressure generated by actuating the master brake cylinder causes a pressure increase in the wheel brake cylinder by shifting partial pressure medium quantities in the brake line.
  • the displaced pressure medium enters the valve seat 29 coming from the stepped bore 28 and leaves it under the flow around the closing member 24 as a hollow-cone-shaped pressure medium jet.
  • valve sub-chamber 43 This causes a back pressure in the valve sub-chamber 43, which is transmitted through the first pressure medium channel 45, but due to the closed second seat valve 54 cannot have any effect in the control chamber 46.
  • the pressure medium entering the valve chamber 43 acting as storage space leaves the radial gap 39 reversing its flow direction and reaches the pressure medium outlet through the axial gap 40 and the valve chamber 35.
  • the pressure medium takes its way in the reverse flow direction through the axial gap 40 and the opened first seat valve 30 in the direction of the master brake cylinder and through the check valve 58 arranged parallel to the valve 10.
  • the valve 10 When braking with a risk of locking, the valve 10 is switched to the working position by energizing the solenoid 17, in which the first seat valve 30 is moved into its closed position by moving the magnet armature 21 against the force of the return spring 31, while the second seat valve 54 den releases first pressure medium channel 45.
  • the outlet valve in the return line (see FIG. 1 in DE 39 34 771 Cl) is switched into the passage position and the return pump is started.
  • the exhaust valve remains in the closed position while valve 10 is no longer energized. This causes the armature 21 to move due to the action of hydraulic forces and the return spring 31 in the direction of the control chamber 46, so that the closing member 24 begins to release the valve seat 29 and the first seat valve 30 is opened. Due to the pressure reduction in the wheel brake cylinder, there is a pressure drop between the inlet side and the outlet side of the first seat valve 30. The lower pressure on the outlet side is also effective through the second pressure medium channel 48 on the front side 49 of the magnet armature 21 near the closing element.
  • the back pressure generated by the master cylinder on the master cylinder side is additionally effective in the valve part chamber 43 through the first pressure medium channel 45 and the second seat valve 54 in the open position in the control chamber 46.
  • the circumferential sealing of the magnet armature 21 prevents pressure equalization between the two end faces 47 and 49 of the magnet armature.
  • the non-pressure-balanced magnet armature 21 is therefore subject to a force opposing the return spring 31, which causes the magnet armature 21 with its valve tappet 22 to assume a position between the closed position and the open position of the first seat valve 30.
  • the resulting reduction in the flow cross-section of the first seat valve 30 results in a throttling of the pressure medium flow with a slower pressure increase in the wheel brake cylinder. If the pressure drop is sufficient, the valve 10 regulates the flow rate to a largely constant extent because a higher differential pressure causes a larger dynamic pressure with a resulting reduction in the flow rate. Cut on the first seat valve 30 and vice versa. As the pressure drop subsides, the dynamic pressure in the valve part chamber 43 also decreases. The return spring 31 returns the armature 21 to its rest position, in which the second seat valve 54 is closed. The valve 10 now releases its full flow section in the first seat valve 30 for the subsequent normal braking. However, if braking is terminated by relieving the pressure on the master brake cylinder when the flow cross-section of the first seat valve 30 is reduced, the pressure medium can also flow out of the wheel brake cylinder through the check valve 58 without delay.
  • the sensitivity of the valve 10 in the direction of smaller pressure drops can be increased by the variant of the first seat valve 30 with guide body 38 shown in FIG.
  • the valve body 27 is provided with a peg-shaped projection 27 ′ directed against the valve tappet 22.
  • This approach 27 ' has the valve seat 29.
  • the guide body 38 is axially extended beyond the closing member 24 and engages around the shoulder 27 'to form a second radial gap 39'.
  • the first radial gap 39 and the axial gap 40 are also present in this variant.
  • the second radial gap 39 ' causes an increase in the dynamic pressure in the valve sub-chamber 43 compared to the previously described first embodiment.

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Electromagnetism (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention vise à obtenir, après la fermeture d'une vanne, un réglage automatique fiable entraînant la réduction d'une section transversale de passage. La vanne (10) comporte un noyau magnétique (21) déplaçable longitudinalement dans un dôme de vanne (14) et son poussoir (22) porte l'élément de fermeture (24) d'une première soupape à siège (30) ouverte en position de repos. La première soupape à siège (30) se trouve dans une chambre de soupape (35) d'où partent deux canaux à fluide hydraulique (45 et 46) qui mènent jusqu'aux faces (47 et 49) du noyau magnétique (21) qui est rendu étanche côté circonférentiel. La communication entre le canal à fluide hydraulique (45) et une chambre de commande (46) située entre la face (47) du noyau magnétique (21) qui est éloignée de l'élément de fermeture (24) et le dôme de vanne (14), est ouverte ou fermée par une seconde soupape à siège (54) qui est fermée en position de repos. Lorsque la seconde soupape à siège (54) est en position ouverte, la pression régnant dans la chambre de commande (46) éloignée de l'élément de fermeture (24) entraîne un déplacement du noyau magnétique (21) à l'encontre de la force exercée par un ressort de rappel (31), ce qui produit une réduction de la section transversale de passage de la première soupape à siège (30). Cette vanne (10) s'utilise tout particulièrement dans des systèmes de freinage hydrauliques antipatinage pour automobiles.
EP94926102A 1993-09-23 1994-09-17 Vanne electromagnetique, notamment pour systemes de freinage hydrauliques antipatinage pour automobiles Withdrawn EP0720549A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4332371A DE4332371A1 (de) 1993-09-23 1993-09-23 Elektromagnetisch betätigbares Ventil, insbesondere für schlupfgeregelte hydraulische Bremsanlagen in Kraftfahrzeugen
DE4332371 1993-09-23
PCT/DE1994/001075 WO1995008460A1 (fr) 1993-09-23 1994-09-17 Vanne electromagnetique, notamment pour systemes de freinage hydrauliques antipatinage pour automobiles

Publications (1)

Publication Number Publication Date
EP0720549A1 true EP0720549A1 (fr) 1996-07-10

Family

ID=6498414

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94926102A Withdrawn EP0720549A1 (fr) 1993-09-23 1994-09-17 Vanne electromagnetique, notamment pour systemes de freinage hydrauliques antipatinage pour automobiles

Country Status (6)

Country Link
US (1) US5645325A (fr)
EP (1) EP0720549A1 (fr)
JP (1) JPH09503178A (fr)
KR (1) KR960703380A (fr)
DE (1) DE4332371A1 (fr)
WO (1) WO1995008460A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4438336A1 (de) * 1994-10-27 1996-05-02 Bosch Gmbh Robert Magnetventil mit Druckbegrenzung für schlupfgeregelte Kraftfahrzeug-Bremsanlagen
JP4016298B2 (ja) * 1996-12-02 2007-12-05 アイシン精機株式会社 ブレーキ液圧制御装置
DE19744317C2 (de) * 1997-10-08 2001-04-19 Lucas Automotive Gmbh Ventilanordnung
US6247766B1 (en) * 1999-05-04 2001-06-19 Delphi Technologies, Inc. Brake control system with an isolation valve
US6302499B1 (en) * 1999-12-29 2001-10-16 Kelsey-Hayes Company Control valve for a hydraulic control unit of vehicular brake systems
DE10321413B4 (de) * 2003-05-13 2014-06-26 Robert Bosch Gmbh Elektromagnetisch betätigbares Ventil
DE102008026121B3 (de) * 2008-05-30 2009-10-15 Rausch & Pausch Gmbh Federgespannter Kolbenspeicher mit Rastierfunktion
DE102008026124B3 (de) * 2008-05-30 2010-02-11 Rausch & Pausch Gmbh Federgespannter Kolbenspeicher mit Rastierfunktion
GB2476075A (en) * 2009-12-10 2011-06-15 Dennis Majoe Solenoid operated valve
KR101617802B1 (ko) 2014-10-30 2016-05-03 현대모비스 주식회사 감압 솔레노이드 밸브

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2505281A1 (fr) * 1981-05-08 1982-11-12 Dba Modulateur de freinage pour systeme de freinage anti-patinant
DE3802648A1 (de) * 1988-01-29 1989-08-10 Mainz Gmbh Feinmech Werke Elektromagnetisch betaetigtes, hydraulisches schnellschaltventil
DE3934771C1 (fr) * 1989-10-18 1991-03-28 Lucas Industries P.L.C., Birmingham, West Midlands, Gb
DE9014763U1 (de) * 1990-10-25 1991-01-10 Schultz, Wolfgang E., Dipl.-Ing., 8940 Memmingen Elektromagnet
DE4132471A1 (de) * 1991-09-30 1993-04-01 Bosch Gmbh Robert Elektromagnetbetaetigtes ventil, insbesondere fuer hydraulische bremsanlagen von kraftfahrzeugen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9508460A1 *

Also Published As

Publication number Publication date
JPH09503178A (ja) 1997-03-31
KR960703380A (ko) 1996-08-17
DE4332371A1 (de) 1995-03-30
US5645325A (en) 1997-07-08
WO1995008460A1 (fr) 1995-03-30

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