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WO1999043523A1 - Electrovanne - Google Patents

Electrovanne Download PDF

Info

Publication number
WO1999043523A1
WO1999043523A1 PCT/EP1999/001195 EP9901195W WO9943523A1 WO 1999043523 A1 WO1999043523 A1 WO 1999043523A1 EP 9901195 W EP9901195 W EP 9901195W WO 9943523 A1 WO9943523 A1 WO 9943523A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure medium
closing member
housing
piston
Prior art date
Application number
PCT/EP1999/001195
Other languages
German (de)
English (en)
Inventor
Diogenes Perez-Cuadro
Josef Lauer
Original Assignee
Continental Teves Ag & Co. Ohg
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 DE19849877A external-priority patent/DE19849877A1/de
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO1999043523A1 publication Critical patent/WO1999043523A1/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
    • B60T8/50—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
    • B60T8/36—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

Definitions

  • the invention relates to an electromagnetic valve according to the preamble of patent claim 1.
  • an electromagnetic valve has already emerged which is provided with an axially movable valve closing member which is attached to a magnet armature and which is arranged in the valve housing. Furthermore, a hydraulically actuated, axially movable valve piston is arranged in the valve housing.
  • the valve piston has an orifice bore, which is located n row to a valve seat to be closed by the valve closing member.
  • the valve housing also has a first and a second pressure medium connection, which are connected without throttles in the basic position of the valve piston and with a throttle in the electromagnetic valve switching position via the orifice bore.
  • valve piston is guided in a liquid-tight housing fit and the hydraulic pressure application for the proper functioning of the valve piston is inevitably determined by the direction of flow through the valve, there are structural and functional restrictions which can be disadvantageous.
  • FIG. 2 shows an alternative design of the valve piston essential for the subject matter of the invention with reference to FIG. 1,
  • FIG. 3 shows a further functional configuration of the valve piston shown in FIG. 2,
  • Fig. 4 shows an electromagnetic valve in the non-excited
  • FIG. 5 shows a modification of the electromagnetic valve according to FIG. 4 with interchanged pressure medium connections.
  • valve housing 7 is designed in a cartridge design, which receives a push-shaped valve closing member 6, which is fastened by means of a press connection to a magnet armature 1, which is guided in a dome-shaped valve sleeve 20.
  • a valve piston 5 which is guided in it with play and which is provided with an orifice bore 4.
  • the orifice bore 4 is in series with a valve seat 14 to be closed by the valve closing member 6.
  • a circumference of the valve piston 5 is at least one generously dimensioned longitudinal groove 15, which, regardless of the position of the valve piston 5, provides a pressure medium connection between the one below and the one above the valve piston 5 guaranteed in the valve housing 7 located pressure medium space.
  • the magnet armature 1 is in the electromagnetically non-energized basic position, in which the orifice bore 4 in the valve piston 5 which throttles the pressure medium flow between the two pressure medium connections 2, 3 in the valve housing 7 is closed by the valve closing member 6. It is further provided according to the invention that for the throttle-free connection of the two pressure medium connections 2, 3, a further pressure medium passage 21 to be closed by the valve piston 5 is provided in the valve housing 7, which, according to the illustration, is released in the basic position of the electromagnetic valve shown.
  • kers 1 is closed by the downward lifting movement of the valve closing member 6 not only the orifice bore 4, but also the further pressure medium passage 21, since the valve closing member 6 presses the upstream valve piston 5 onto the housing stage 13 delimiting the pressure medium passage 21 in the valve housing 7.
  • pressure medium thus passes via the first pressure medium connection 2, which opens approximately axially into the valve housing 7, into the pressure medium space located below the longitudinal groove 15 and via the longitudinal groove 15 without throttling into the housing cavity located above the longitudinal groove 15, which, as previously described, passes through the aperture bore 4 establishes a hydraulic connection to the second pressure medium connection 3. Accordingly, there is the closure of the pressure medium passage 21 on the valve piston side and the hydraulic pressure 5 -
  • the compression spring 8 acting in the direction of the valve closing member 6 has a substantially lower pretensioning force than the magnet armature compression spring 9 which positions the magnet armature 1 in the basic position.
  • the force of the compression spring 8 is a multiple, for example 7 times the force of the above-mentioned Magnet armature spring
  • the compression spring 8 is designed such that an undesirable, so-called closing and thus the unintentional closing of the pressure medium passage 26 is prevented by means of the valve piston 5.
  • the magnet armature pressure adjusting spring 9 is able to position the magnet armature 1 in the basic position even under a fluid high pressure of approximately 300 bar.
  • the magnet armature 1, the valve housing 7, the valve closing element 6, the valve piston 5, the magnet armature pressure adjusting spring 9 and the pressure spring 8 are arranged coaxially to one another in a largely rotationally symmetrical design.
  • the cartridge-shaped valve housing 7 in the area of the block-shaped receiving body is designed in two parts in order to appropriately mount the valve piston 5, the compression spring 8 and the rod filter 17 located below the valve piston 5 enable, which is used instead of an Rm filter shown in the following figures.
  • valve piston 5 is guided in the upper half of the housing along its jacket surface interrupted by the longitudinal groove 15, while the lower part of the valve housing accommodates the pressure medium connection 2, which approximately merges at an angle, and the pressure medium connection 3, which is approximately radially rounded.
  • the rod filter 17 is accordingly arranged between the two pressure medium connections 2, 3 in the center of the valve axis in an extension of the stepped bore receiving the valve piston 5.
  • the bypass bore 16, which encloses the valve housing 7, m connects to the plate-shaped check valve 10 arranged at the bottom of the valve housing 7, with a corresponding pressure reduction in the area of the plate filter 18, bypassing the valve piston 5 between the two pressure medium connections 2, 3.
  • a ball check valve which is known per se and which is likewise delimited coaxially to the bypass bore 16 by the plate filler 18 shown in the figure.
  • the compression spring 8 could then be used with a correspondingly smaller winding diameter m, the bore section of the rod filter 17 and, if necessary, the pressure medium connection 3 could be protected against contamination by means of an Rmg filter.
  • the bypass bore 16 and the pressure medium connection 2 are directly connected to a pressure medium source, which corresponds to the brake pressure sensor when the electromagnetic valve is used for a wheel slip-controlled brake system.
  • the pressure medium connection 3 directed approximately obliquely out of the valve housing 7 would be correspondingly connected to the wheel slip-controlled wheel brakes in the present application, whereby the proposed electromagnetic valve takes over the function of a de-energized, pressure-modulating inlet valve which forms a noise-reduced orifice valve by means of the structurally and functionally explained valve piston.
  • the flow through the solenoid valve can also take place in the opposite direction, so that in the latter application the brake pressure transmitter is connected to the pressure medium connection 3 and the wheel brake to the pressure medium connection 2. This results in a relatively simple drilling of the valve housing 7, since the pressure medium connection 3 opens into the valve housing 7 coaxially to the valve axis. 2 differs from FIG.
  • valve plate 22 with a relatively large passage opening, which is also aligned coaxially to the valve axis.
  • the valve piston 5 located between the valve plate 22 and the tappet-shaped valve closing member 6 is characterized by a particularly thin-walled, reduced-mass design, which can be produced inexpensively by deep drawing, pressing or plastic injection molding.
  • the sleeve-shaped valve piston part has a thick-walled insert part 11 which contains the orifice bore 4 and whose cap-shaped projection 12 is directed towards the through bore ⁇ .
  • a fixed orifice is also pressed in below the valve plate 22 or firmly connected to the valve plate 22, which can be designed as a cascade orifice if required.
  • the essential features of the electromagnetic valve shown in FIG. 2 do not differ from the detailed description of the object according to FIG. 1, so that reference is made to FIG. 1 with regard to the features not mentioned in relation to FIG. 2 - 9
  • FIG. 3 shows a partial illustration of the previously described insert part 11, which can be provided with a check valve 10 if desired or required.
  • the check valve 10 is designed as a ball check valve, with the ball in a transverse channel
  • FIG. 4 shows, while maintaining the details already known from FIG. 1, a constructive extension in the area of the valve piston 5, on which a sleeve-shaped cage is provided
  • the basic position of the valve enables the opening of the orifice bore 4.
  • the stop disk 25 bears against a shoulder of the push-button-shaped valve closing element 6 under the action of the spring 26 supported on the valve piston 5.
  • the inner shoulder of the cage 24 rests on the stop disk 25.
  • the biasing force of the compression spring 8 which is supported between the valve piston 5 and the housing stage 13 is considerably smaller than the spring 26 which acts in the opposite direction in the cage 24.
  • the valve according to FIG. 5 differs from the valve according to FIG. 4 by the interchanged connection diagram of the pressure medium channels in the valve block and thus by the reverse flow through the pressure medium connections 2, 3. Consequently, a pressure medium sensor, for example, is included at the height of the valve piston 5 Brake pressure sensor for a wheel slip-controlled brake system, while below the valve piston 5 at the pressure medium passage 2 there is a connection for a pressure medium receiver, for example for a pump, which is connected to a slip-controlled wheel brake.
  • a pressure medium sensor for example, is included at the height of the valve piston 5 Brake pressure sensor for a wheel slip-controlled brake system, while below the valve piston 5 at the pressure medium passage 2 there is a connection for a pressure medium receiver, for example for a pump, which is connected to a slip-controlled wheel brake.
  • This illustration shows that the electromagnetic valve described in FIG. 4 can be used universally without having to change the basic structure of the valve.
  • solenoid valves described are characterized by the selected design by a low-noise, easily ventilated, flow-efficient and independent of hydraulic pressure fluctuations in operation.
  • Magnet armature pressure spring 0 check valve 1 insert 2 projection 3 housing stage 4 valve seat 5 longitudinal groove 6 bypass bore 7 rod filter 8 plate filter 9 housing 0 valve sleeve 1 pressure medium passage 2 valve plate 3 cross channel 4 cage 5 stop disk 6 spring

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

Abstract

L'invention concerne une électrovanne comportant un élément de fermeture (6) monté mobile dans le sens axial dans un corps de soupape (7) et pilotant une liaison de fluide hydraulique, qui est monté sur une armature (1). Cette électrovanne comporte également un piston de soupape (5) à actionnement hydraulique monté dans le corps de soupape (7), de manière à se déplacer dans le sens axial par rapport à l'élément de fermeture (6). Ce piston de soupape (5) comporte un trou borgne (4) aligné par rapport à un siège de soupape (14) devant être fermé par l'élément de fermeture (6). Il est prévu dans le corps de soupape (7) un premier et un second raccord pour fluide hydraulique (2 3), qui sont interconnectés en position de base du piston de soupape (5), sans étranglement. En position de base de l'armature (1), où il n'y a pas d'excitation électromagnétique, le trou borgne qui étrangle le flux de fluide hydraulique entre les deux raccords pour fluide hydraulique (2,3), est fermé dans le piston de soupape (5) par l'élément de fermeture (6). Pour assurer une liaison sans étranglement entre les deux raccords pour fluide hydraulique (2,3), il est prévu dans le corps de soupape (7) un autre passage pour fluide hydraulique (21), devant être fermé par le piston de soupape (5) et qui est libéré dans la position de base de l'armature (1), où il n'y a pas d'excitation électromagnétique.
PCT/EP1999/001195 1998-02-28 1999-02-24 Electrovanne WO1999043523A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE19808625.3 1998-02-28
DE19808625 1998-02-28
DE19824526 1998-06-02
DE19824526.2 1998-06-02
DE19849877.2 1998-10-29
DE19849877A DE19849877A1 (de) 1998-02-28 1998-10-29 Elektromagnetventil

Publications (1)

Publication Number Publication Date
WO1999043523A1 true WO1999043523A1 (fr) 1999-09-02

Family

ID=27218178

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1999/001195 WO1999043523A1 (fr) 1998-02-28 1999-02-24 Electrovanne

Country Status (1)

Country Link
WO (1) WO1999043523A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006084526A1 (fr) * 2005-02-08 2006-08-17 Robert Bosch Gmbh Soupape a actionnement electromagnetique, notamment pour des systemes de freinage dans des vehicules automobiles
WO2012038297A1 (fr) * 2010-09-21 2012-03-29 Continental Teves Ag & Co. Ohg Électrovanne, notamment pour des équipements de freinage de véhicule automobile à patinage régulé
DE102018203602A1 (de) * 2018-03-09 2019-09-12 Continental Teves Ag & Co. Ohg Elektromagnetventil, insbesondere für hydraulische, radschlupfgeregelte Kraftfahrzeugbremsanlagen
DE102013217580B4 (de) 2013-09-04 2025-03-27 Continental Automotive Technologies GmbH Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeug- Bremsanlagen

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2138182A1 (de) * 1971-04-28 1972-11-23 Fiat S.P.A., Turin (Italien) Elektrisch gesteuertes Umschaltventil
EP0595014A1 (fr) * 1992-10-29 1994-05-04 Robert Bosch Gmbh Electrovanne
DE4312414A1 (de) * 1993-04-16 1994-10-20 Bosch Gmbh Robert Ventilanordnung für eine Bremsblockierschutz-Einrichtung
DE4339305A1 (de) 1993-06-09 1995-05-24 Teves Gmbh Alfred Elektromagnetventil, insbesondere für hydraulische Bremsanlagen mit Schlupfregelung
WO1996005090A1 (fr) * 1994-08-06 1996-02-22 Itt Automotive Europe Gmbh Dispositif a soupape, notamment pour des systemes de freins hydrauliques equipes d'antiblocage ou et/ou d'antipatinage, et procede de reglage d'un dispositif a soupape
DE19528726A1 (de) * 1994-08-05 1996-03-28 Aisin Seiki Elektromagnetisches Ventil
WO1997008032A1 (fr) * 1995-08-29 1997-03-06 Kelsey-Hayes Company Soupape de regulation a orifice commutable pour systeme abs
DE19700405A1 (de) * 1997-01-09 1998-07-16 Teves Gmbh Alfred Magnetventil

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2138182A1 (de) * 1971-04-28 1972-11-23 Fiat S.P.A., Turin (Italien) Elektrisch gesteuertes Umschaltventil
EP0595014A1 (fr) * 1992-10-29 1994-05-04 Robert Bosch Gmbh Electrovanne
DE4312414A1 (de) * 1993-04-16 1994-10-20 Bosch Gmbh Robert Ventilanordnung für eine Bremsblockierschutz-Einrichtung
DE4339305A1 (de) 1993-06-09 1995-05-24 Teves Gmbh Alfred Elektromagnetventil, insbesondere für hydraulische Bremsanlagen mit Schlupfregelung
DE19528726A1 (de) * 1994-08-05 1996-03-28 Aisin Seiki Elektromagnetisches Ventil
WO1996005090A1 (fr) * 1994-08-06 1996-02-22 Itt Automotive Europe Gmbh Dispositif a soupape, notamment pour des systemes de freins hydrauliques equipes d'antiblocage ou et/ou d'antipatinage, et procede de reglage d'un dispositif a soupape
WO1997008032A1 (fr) * 1995-08-29 1997-03-06 Kelsey-Hayes Company Soupape de regulation a orifice commutable pour systeme abs
DE19700405A1 (de) * 1997-01-09 1998-07-16 Teves Gmbh Alfred Magnetventil

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006084526A1 (fr) * 2005-02-08 2006-08-17 Robert Bosch Gmbh Soupape a actionnement electromagnetique, notamment pour des systemes de freinage dans des vehicules automobiles
WO2012038297A1 (fr) * 2010-09-21 2012-03-29 Continental Teves Ag & Co. Ohg Électrovanne, notamment pour des équipements de freinage de véhicule automobile à patinage régulé
DE102013217580B4 (de) 2013-09-04 2025-03-27 Continental Automotive Technologies GmbH Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeug- Bremsanlagen
DE102018203602A1 (de) * 2018-03-09 2019-09-12 Continental Teves Ag & Co. Ohg Elektromagnetventil, insbesondere für hydraulische, radschlupfgeregelte Kraftfahrzeugbremsanlagen

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