WO2001062566A1 - Electrovanne - Google Patents

Electrovanne Download PDF

Info

Publication number
WO2001062566A1
WO2001062566A1 PCT/EP2001/001938 EP0101938W WO0162566A1 WO 2001062566 A1 WO2001062566 A1 WO 2001062566A1 EP 0101938 W EP0101938 W EP 0101938W WO 0162566 A1 WO0162566 A1 WO 0162566A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
piston
spring
central opening
carrier
Prior art date
Application number
PCT/EP2001/001938
Other languages
German (de)
English (en)
Inventor
Diogenes Perez-Cuadro
Christoph Voss
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 DE10054743A external-priority patent/DE10054743A1/de
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2001062566A1 publication Critical patent/WO2001062566A1/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

Definitions

  • the invention relates to an electromagnetic valve according to the preamble of claim 1.
  • valve piston With its control edge, the valve piston takes over the function of a flow control valve, so that a particularly closely tolerated selection of the fit clearance is required for leak-free sealing of the valve piston in the valve housing.
  • the associated manufacturing outlay is accordingly great.
  • the solenoid valve should be switchable as a two-position valve or as an solenoid valve which can be actuated in an analogous manner.
  • FIG. 1 shows a first embodiment of the electromagnetic valve according to the invention in cross section
  • FIG. 2 shows an alternative embodiment of the electromagnetic valve according to FIG. 1 with a modified valve tappet and valve piston design
  • FIG. 3 shows a modification of the electromagnetic valve according to FIG. 1 with a valve housing section designed as a deep-drawn part
  • FIG. 5 shows a modification of the electromagnetic valve known from FIG. 4 with a lower housing part made of thin sheet metal.
  • FIG. 1 shows a first embodiment of the solenoid valve according to the invention, which is normally closed in the normal position and which has a valve housing 12 in which a valve tappet 2, which is attached to a magnet armature 6, is arranged, with its end facing away from the magnet armature 6 onto a spring-loaded valve piston 4 is directed which is guided in a sleeve-shaped piston carrier 3. Furthermore, there is a central opening 1 for the hydraulic connection of an inlet channel 14 to an outlet channel 15 in the piston carrier 3. The central opening 1 is arranged in alignment with the valve tappet 2 and the other valve components in the piston carrier 3.
  • the end face of the spring-loaded valve piston 4 keeps the central opening 1 closed in the function of a seat valve in a pressure-tight manner.
  • the valve tappet 2 lifts the valve piston 4 against a valve seat surface 7 of the piston carrier 3 delimiting the central opening 1 against the action of the tied spring 5.
  • the piston carrier 3 is formed from a cup-shaped sleeve, the central opening 1 being arranged in the pot bottom as a calibrated pressure medium bore.
  • the central opening 1 is delimited by the already mentioned valve seat surface 7, which is designed as a conical sealing seat instead of a plate sealing seat.
  • the sleeve-shaped piston carrier 3 is adapted in the inner diameter to the outer diameter of a spring stop 8 and to the outer diameter of the valve piston 4, the spring stop 8 being provided with an interference fit with respect to the piston carrier 3 and the valve piston 4 with a clearance fit.
  • the piston carrier 3, the valve piston 4, the spring 5 and the spring stop 8 advantageously form an independently manageable, functionally preassembled and pretested assembly of the electromagnetic valve.
  • the valve piston 4 is raised on the piston head to form a valve closing element 4 in the direction of the central opening 1 provided in the piston carrier 3 in a substantially conical shape to the valve seat surface 7 delimiting the central opening 1.
  • the valve piston 4 has a recess 9 in the form of a longitudinal slot on the piston shaft, which has a permanent hydraulic connection to the pressure medium spaces 10, 11 located directly on both sides of the valve piston 4 in the piston carrier 3.
  • a compression spring 17 pushed onto the valve tappet 2 acts between a valve housing stage 13 and the magnet armature 6, so that the magnet armature 6 is normally lifted off the valve tappet 2 from the valve closing member 4 '.
  • the valve lifter 2 and the valve piston 4 are made of a metal.
  • the valve housing 12 which is designed as a solid rotating part (cartridge), is provided with a stepped bore which decreases in diameter in the direction of the valve tappet 2 and at the largest bore step of which the bottom of the piston of the piston carrier 3 abuts.
  • a cohesive connection in the form of a weld 16 at the level of the disk-shaped spring stop 8 serves as permanent fixation of the piston carrier 3 in the stepped bore.
  • the deep-drawn edge of the spring stop 8 forms a press connection with the inner wall of the piston carrier 3.
  • valve piston 4 The between the valve piston 4 and the spring stop 8 arranged spring 5 is designed as a helical spring with great spring stiffness in order to ensure safe closing under all operating conditions and, if desired or required, to achieve a desired partially open valve intermediate position.
  • the relatively stiff spring 5 makes it possible to dispense with a proportional magnet and ensures safe operation under small hydraulic pressure differences on the valve piston 4 if the valve piston 4 is to be operated in the electromagnetic excitation not only as a two-position valve but also as an analog valve in various partial open positions.
  • the compression spring 17 arranged between the bore step in the valve housing 2 and the magnet armature 6 lent their stiffness designed to be relatively soft, just to overcome the friction between the magnet armature 6 and the valve housing 12 after the termination of electromagnetic excitation.
  • valve closing member 4 ⁇ on the valve piston 4 and the tip of the valve tappet 2 there is a slight axial play in the closed valve switching position in order to ensure that the valve piston 4 closes securely when de-energized, regardless of thermally induced changes in length of the parts, signs of wear on the valve seat surface 7 and possible component tolerances to ensure.
  • the electromagnetic valve according to FIG. 2 differs from the electromagnetic valve according to FIG. 1 in that it has a relatively solid piston carrier 3, which is designed as a rotating part, and which therefore does not represent an alternative to the valve seat plate explained in FIG. 1, which can be used when required, and generally does not show any signs of wear always represents recessed valve seat 7. Furthermore, the electromagnetic valve according to FIG. 2 differs from FIG. 1 by the direct support of the compression spring 17 between a step of the valve tappet 2 and the cup base of the piston carrier 3, so that the number of bore stages in the valve housing is greater than that of the electromagnetic valve according to FIG. 1 12 can be significantly reduced.
  • the biasing force of the compression spring 17 can be adjusted very precisely by moving the piston carrier 3 in the stepped bore, the piston carrier 3 being securely fixed to the valve housing 12 by means of a weld 16 after the adjustment.
  • the selected arrangement also enables a particularly short compression spring 17, which is placed over the valve tappet 2, with comparatively few spring windings.
  • the valve lifter 2 is preferably made of plastic, so that thereby the weight, friction, wear and resulting noise reducing effects.
  • the electromagnetic valve according to FIG. 3 differs from the electromagnetic valves according to FIGS. 1 and 2 essentially by the simplification of the valve housing 12, which is designed in the area of the piston carrier 3 as a deep-drawing sleeve, so that the deep-drawn piston carrier 3 with the spring 5 and the deep-drawn valve piston 4 forms a prefabricated and preset assembly module, into which a solid tubular magnetic core 18 is inserted to a stop, which is fastened to its collar by means of an external caulking 19 in the valve receiving body 20 in a pressure-tight manner.
  • the sleeve-shaped valve housing 12 is sealed in the direction of the outlet channel 15 by means of an O-ring 21 inserted into the stepped bore of the valve receiving body 20, so that the one known from FIGS.
  • valve housing 12 designed as a pot-shaped deep-drawing sleeve, first accommodates the spring 5, then the valve piston 4, then the piston carrier 3, which is to be set to the desired pretensioning force of the spring 5, and finally, after the welding 16, the magnetic core 18.
  • FIG. 4 a solenoid valve is shown, the valve housing 'is the same as in FIGS. 1 and 2 in the area of the magnetic core 18 made of mild steel and the valve accommodating member 20 caulked 12 while maintaining the massive rotary part execution.
  • the spring element 23 thus takes over the function of the spring 5 known from FIGS. 1 to 3.
  • the outer edge of the spring element 23 is supported on a shoulder of the retaining ring 22 pressed into the piston carrier 3 from below, while in the area of the center of the surface of the spring element 23 the ram-shaped extension of the valve piston 4 rests.
  • the spring 5 designed as a helical spring now has only low spring stiffness, which is supported on the offset polygonal profile of the valve piston 4.
  • the polygonal profile is designed such that a recess 9 remains on the circumference of the valve piston 4 for the pressure medium to pass through.
  • the valve piston 4 is preferably made of a plastic. It is 4 ⁇ im to form the valve closing member Head area tapered and rounded at the tip.
  • the spring element 23 presses the valve closing member ⁇ against the conical valve seat surface 7 of the piston carrier 3, while the valve tappet 2 projects into the central opening 1 and, according to the illustration, comes to rest on the valve closing member 4 ⁇ .
  • valve housing 12 which, in the area of use of the valve receiving body 20, consists only of a thin sheet metal deep-drawn part which is welded to the tubular magnetic core 18 and whose collar 24 is directly in the stepped bore of the valve receiving body 20 is held by an external caulking 19. Otherwise, the construction of the electromagnetic valve according to FIG. 5 corresponds to the electromagnetic valve according to FIG. 4.
  • All of the solenoid valves of FIGS. 1 to 5 have in common that they are functionally designed as normally closed solenoid valves, each of which accommodates a preassembled, pre-testable and independently manageable seat valve assembly in its valve housings 12.
  • the exact setting of the spring forces takes place by means of force measurement, which creates the prerequisite for a simple, proportional actuation of the valve piston 4.
  • the selected construction advantageously allows the stroke of the valve piston 4 to be chosen to be relatively large and the valve piston 4 can be easily centered in the piston carrier 3 in a simple manner.
  • the piston carrier 3 is designed such that it can be used universally, ie regardless of whether the valve housing 12 now consists of a deep-drawn part or a solid turned part.
  • valve tappet 2 begins to lower in the direction of the valve closing member 4 ⁇ .
  • the valve tappet 2 presses the valve piston 4 against the action of the spring 5 correspondingly more or less far away from the valve seat surface 7, so that this on the inlet channel 14, on the ring filter 26 and the high-pressure medium present in the transverse channel 25 passes through the central opening 1 into the pressure medium chamber 11 and from there along the recess 9 through the pressure medium chamber 10 to the outlet channel 15.
  • valve piston 4 Regardless of the proportional actuation of the valve piston 4, this is of course also a two-position valve, i.e. switchable to the closed or fully open valve position.
  • the functioning of the electromagnetic valves according to FIGS. 4 and 5 differ from the electromagnetic valves of FIGS. 1-3 in that the valve is reset without axial play. tilkolbens 4 in the closed basic valve position, without that the lifting of the valve lifter 2 is forced from the valve closing member 4 '.
  • Another advantage arises from the characteristics of the rigid spring element 23, whereby the range of excitation currents available for the proportional control of the electromagnetic valve can be increased in order to refine the controllability of the valve piston 4 in the desired intermediate positions.
  • the electromagnetic valves shown in FIGS. 1-5 are thus distinguished according to the invention by a particularly simple, robust construction. Due to the selected centering of the valve piston 4 in the piston carrier 3 and the arrangement of the springs 5, 23, the valve piston 4 can in each case be adjusted simply and precisely by means of force measurement in a preassembled valve assembly, proportional proportional control being favored by the large practicable stroke of the valve piston 4.

Landscapes

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

Abstract

L'invention concerne une électrovanne comportant une cage de soupape (12) dans laquelle est disposé un poussoir de soupape (2) qui est monté sur un noyau magnétique (6) et est dirigé par son extrémité opposée au noyau magnétique (6) vers un piston à soupape (4) sollicité par ressort. Ledit piston est guidé dans un support de piston (3) sous forme de manchon. L'électrovanne comprend également une ouverture centrale (1) pour assurer la communication hydraulique d'un conduit d'admission (14) avec un conduit de sortie (15) dans la cage de soupape (12). L'ouverture centrale (1) est placée à fleur du poussoir de soupape (2) dans le support de piston (3). Lorsque la soupape est en position de base, la face avant du piston (4) sollicité par ressort dans la fonction d'une soupape à siège maintient l'ouverture centrale (1) fermée, de manière étanche au milieu hydraulique, alors que lors de l'excitation électromagnétique du noyau magnétique (6), le poussoir de soupape (2) soulève le piston de soupape (4) à l'encontre de l'action du ressort, d'une surface de siège de soupape délimitant l'ouverture centrale (1).
PCT/EP2001/001938 2000-02-25 2001-02-21 Electrovanne WO2001062566A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE10008798.1 2000-02-25
DE10008798 2000-02-25
DE10028815 2000-06-10
DE10028815.4 2000-06-10
DE10054743.5 2000-11-04
DE10054743A DE10054743A1 (de) 2000-02-25 2000-11-04 Eletromagnetventil

Publications (1)

Publication Number Publication Date
WO2001062566A1 true WO2001062566A1 (fr) 2001-08-30

Family

ID=27213682

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2001/001938 WO2001062566A1 (fr) 2000-02-25 2001-02-21 Electrovanne

Country Status (1)

Country Link
WO (1) WO2001062566A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1623900A1 (fr) * 2004-08-07 2006-02-08 Robert Bosch GmbH Dispositif de soupape
EP2196637A1 (fr) * 2008-12-13 2010-06-16 Schaeffler KG Unité hydraulique et soupape hydraulique faisant partie de cette unité hydraulique
CN102753871A (zh) * 2009-12-21 2012-10-24 罗伯特·博世有限公司 用于安装在安装块中的可电磁切换的阀
CN105425897A (zh) * 2015-11-20 2016-03-23 宁波弗莱格液压有限公司 一种电磁定位手柄
CN112032391A (zh) * 2020-09-17 2020-12-04 上海百图低温阀门有限公司 一种用于汽车升压系统的低温电磁阀
DE102018114238B4 (de) 2017-06-14 2023-04-27 Bwi (Shanghai) Co., Ltd. Gesteuertes Bremsmagnetventil

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2909504A1 (de) * 1978-05-20 1980-09-18 Bosch Gmbh Robert Magnetventil
JPS60252053A (ja) * 1984-05-30 1985-12-12 Honda Motor Co Ltd アンチロツク制御装置のモジユレ−タ
EP0218823A1 (fr) * 1985-10-18 1987-04-22 AlliedSignal Inc. Soupape antipatinage pour système de freinage assisté
DE3634349C1 (de) * 1986-10-09 1987-05-21 Daimler Benz Ag Baugruppe aus mehreren unabhaengig voneinander elektromagnetisch schaltbaren Wegeventilen
WO1995012509A1 (fr) * 1993-11-05 1995-05-11 Itt Automotive Europe Gmbh Soupape regulatrice de pression
DE4427905A1 (de) 1994-08-06 1996-02-08 Teves Gmbh Alfred Ventilvorrichtung, insbesondere für hydraulische Bremsanlagen mit Blockier- und/oder Antriebsschlupfregelung
WO1996004160A1 (fr) * 1994-08-05 1996-02-15 Itt Automotive Europe Gmbh Systeme de freinage hydraulique a regulation antipatinage
DE4445221A1 (de) * 1994-12-17 1996-06-20 Bosch Gmbh Robert Elektromagnetisch betätigtes Ventil, insbesondere für schlupfgeregelte hydraulische Bremsanlagen in Kraftfahrzeugen

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2909504A1 (de) * 1978-05-20 1980-09-18 Bosch Gmbh Robert Magnetventil
JPS60252053A (ja) * 1984-05-30 1985-12-12 Honda Motor Co Ltd アンチロツク制御装置のモジユレ−タ
EP0218823A1 (fr) * 1985-10-18 1987-04-22 AlliedSignal Inc. Soupape antipatinage pour système de freinage assisté
DE3634349C1 (de) * 1986-10-09 1987-05-21 Daimler Benz Ag Baugruppe aus mehreren unabhaengig voneinander elektromagnetisch schaltbaren Wegeventilen
WO1995012509A1 (fr) * 1993-11-05 1995-05-11 Itt Automotive Europe Gmbh Soupape regulatrice de pression
WO1996004160A1 (fr) * 1994-08-05 1996-02-15 Itt Automotive Europe Gmbh Systeme de freinage hydraulique a regulation antipatinage
DE4427905A1 (de) 1994-08-06 1996-02-08 Teves Gmbh Alfred Ventilvorrichtung, insbesondere für hydraulische Bremsanlagen mit Blockier- und/oder Antriebsschlupfregelung
DE4445221A1 (de) * 1994-12-17 1996-06-20 Bosch Gmbh Robert Elektromagnetisch betätigtes Ventil, insbesondere für schlupfgeregelte hydraulische Bremsanlagen in Kraftfahrzeugen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 010, no. 126 (M - 477) 10 May 1986 (1986-05-10) *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1623900A1 (fr) * 2004-08-07 2006-02-08 Robert Bosch GmbH Dispositif de soupape
EP2196637A1 (fr) * 2008-12-13 2010-06-16 Schaeffler KG Unité hydraulique et soupape hydraulique faisant partie de cette unité hydraulique
CN102753871A (zh) * 2009-12-21 2012-10-24 罗伯特·博世有限公司 用于安装在安装块中的可电磁切换的阀
CN102753871B (zh) * 2009-12-21 2015-11-25 罗伯特·博世有限公司 用于安装在安装块中的可电磁切换的阀
CN105425897A (zh) * 2015-11-20 2016-03-23 宁波弗莱格液压有限公司 一种电磁定位手柄
DE102018114238B4 (de) 2017-06-14 2023-04-27 Bwi (Shanghai) Co., Ltd. Gesteuertes Bremsmagnetventil
CN112032391A (zh) * 2020-09-17 2020-12-04 上海百图低温阀门有限公司 一种用于汽车升压系统的低温电磁阀

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