WO2007057438A1 - Soupape hydraulique - Google Patents

Soupape hydraulique Download PDF

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Publication number
WO2007057438A1
WO2007057438A1 PCT/EP2006/068593 EP2006068593W WO2007057438A1 WO 2007057438 A1 WO2007057438 A1 WO 2007057438A1 EP 2006068593 W EP2006068593 W EP 2006068593W WO 2007057438 A1 WO2007057438 A1 WO 2007057438A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
magnetic coil
valve housing
housing
armature
Prior art date
Application number
PCT/EP2006/068593
Other languages
German (de)
English (en)
Inventor
Christoph Voss
Harald Biller
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
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2007057438A1 publication Critical patent/WO2007057438A1/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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0651—One-way valve the fluid passing through the solenoid coil
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F7/1607—Armatures entering the winding

Definitions

  • the invention relates to a hydraulic valve according to the preamble of patent claim 1.
  • the valve housing receives a cooperating with a magnet armature valve closure member which is directed to a valve seat in the valve housing.
  • a magnet coil is provided which is arranged outside a sleeve-shaped, non-magnetic valve housing section. Due to the non-magnetic valve housing portion results in a relatively large construction cost and an undesirably large magnetic resistance at the same time a large radial gap extending between the armature and the valve housing.
  • the proposed construction does not allow any reduction in the overall height.
  • FIG. 1 shows an embodiment of the subject invention in the form of a closed in the basic position hydraulic valve
  • FIG. 2 shows an embodiment of the subject invention in the form of a normally open hydraulic valve
  • Figure 3 is a designed as a two-stage valve hydraulic valve in its closed position.
  • Each illustrated in longitudinal section, designed as a 2/2-way valve seat hydraulic valve has a designed in cartridge design valve housing 6 which receives a actuatable by a magnetic armature 3 valve closure member 14 which is concentrically directed to a valve seat 8 in the valve housing 6.
  • a solenoid 1 is integrated directly into the valve housing 6 for actuating the magnet armature 3, which is arranged in a magnetic flux conducting portion 5 of the valve housing 6 and is fixedly connected to this section 5.
  • an axial gap 2 is provided, which is bridged as well as a provided between a lateral surface of the armature 3 and the valve housing 6 radial gap 4 during electromagnetic excitation of magnetic field lines.
  • the valve housing 6 has a magnetic flux conducting further section 7, the liquid-tightly abuts the front side of the magnetic portion 5, wherein the further portion 7 in the lower region of the valve seat 8 and a few pressure medium channels 9, 10 receives.
  • Both sections 5, 7 of the valve housing 6 are designed as firmly connected to each other cartridge-shaped housing halves, in which advantageously the magnetic coil 1 according to the principle of a plunger space-optimized and integrated low resistance with respect to the magnetic field.
  • the solenoid coil 1 is therefore exposed via the pressure medium channels 9, 10 of the in the valve housing 6 under pressure as well as outflowing liquid.
  • At least one of the two cartridge-shaped sections 5, 7 of the valve housing 6, which are designed thick-walled for use in high-pressure hydraulic systems, has for integrating the magnetic coil 1 adapted to the magnetic coil recess 24, in which the solenoid 1 is well received, securely fastened and in the area its inner periphery is acted upon directly by the liquid flowing through the valve housing 6, provided that as a result of the open position of the valve closing member 14, a corresponding pressure supply into the valve housing 6 takes place.
  • the magnet armature 3 thus immersed liquid-flushed in sections in the magnetic coil 1, which is integrated according to Fig. 1-3 in each case in the recess 24 of the section 5.
  • valve housing 6 thus consists only of two cartridge halves, the upper half of the housing is formed by the recess 24 provided with the section 5 and the lower half of the housing through the further section 7, the Valve seat 8 carries.
  • Both sections 5, 7 have, in all embodiments, mutually facing, annular disk-shaped end surfaces, which are connected to each other in a liquid-tight manner by means of a circumferential weld 21.
  • a sealing washer 15 is inserted, which advantageously the liquid-tight from the magnetic coil 1 protruding electrical contact 23 in the direction of the passage opening 13 in the valve housing 6 surrounds.
  • the coil turns and connected to the coil turns contact 23 of the magnetic coil 1 are liquid-tight on all sides surrounded by a plastic, which forms the bobbin.
  • the magnet coil 1 is either fixed in the recess 24 of the section 5 or fixed frictionally or positively via the plastic jacket of the contact 23 in the passage opening 13 of the valve housing 6.
  • the armature 3 has a height / width ratio, the amount equal to or forth is less than one, so that in practice the height of the magnet armature 3 does not necessarily exceed the outer diameter of the magnet armature 3.
  • the recess 24 having portion 5 is formed as a cold impact part, the contour of which can be produced automatically by cold striking a magnetic flux conducting blank from which in a single operation advantageously the outside as well which is formed for receiving the magnetic coil 1 required inner contour.
  • valve seat sleeve 26 having further portion 7 of the valve housing 6 is made as a cold-formed part of a tubular blank whose outer contour has a housing stage with an annular groove 12, in which for the attachment and sealing of the further portion 7 in the valve block 11 with respect to the section 7 softer Material of the valve block 11 is plastically displaced.
  • the magnetic flux conducting two-piece valve housing 6 thus consists in all embodiments of a preferably prepared by cold striking or extrusion of steel blank, so that is dispensed with the previously known from the prior art different machining and deep drawing manufacturing processes for the items of the valve body 6.
  • the magnet armature 3 can also be produced in a simplified manner by extrusion or cold striking.
  • all of the hydraulic valves depicted in FIGS. 1-3 have a filter element 31 arranged at the lower, cone-shaped stepped end of the section 7, which is designed as a ring filter element and prevents dirt from entering the generally calibrated pressure medium channel 9.
  • a filter element 31 arranged at the lower, cone-shaped stepped end of the section 7, which is designed as a ring filter element and prevents dirt from entering the generally calibrated pressure medium channel 9.
  • To reduce the valve height of the pressure medium channel 9 is in Fig. 1, 2 immediately parallel to the pressure medium channel 10 in an intermediate bottom above the peg-shaped stepped (further) section 7 inserted, which is reduced in diameter at the lower pin-shaped end so far that he with relatively low insertion force at the bottom of the valve receiving bore 30 in a channel bore (valve port 39 in Fig.l) or in a valve seat plate 43 (see FIG. 2) sealingly extends.
  • the magnetic core is formed for the closed in the basic position hydraulic valves according to Figures 1 and 3 in section 5 by a centrally formed to the valve longitudinal axis cylinder projection 25 into which from the direction of the axial gap 2, a blind bore 16 opens, which receives a compression spring 17, which between the End face of the armature 3 and the end of the blind bore 16 is clamped, whereby in the basic valve position of the armature 3 rests with the valve closure member 14 on the valve seat 8.
  • the closed in Figure 1 in the basic position hydraulic valve has on the side remote from the compression spring 17 end face of the armature 3, a spherical valve closure member 14 which is pressed under the action of the compression spring 17 against the funnel-shaped valve seat 8.
  • the valve closure member 14 is sunk centrally by means of a capacitor weld in a blind bore 37 of the armature 3.
  • the valve seat sleeve 26 extends with a small clearance in the blind bore 37 so that the armature 3 on the valve seat sleeve 26 has an internal centering.
  • the lateral surface of the blind bore 37 has a longitudinal groove 36, so that in the electromagnetically open valve position a cross-section sufficiently large, low-resistance hydraulic connection between the two valve ports 39 is ensured in the valve block 11.
  • the section 5 at its upper end face on an adapted to the diameter of the magnet armature 3 opening, which is closed by a flat, thin-walled cover 41.
  • the cover 41 has in the middle a sleeve-shaped projection 42 which extends to center the magnet armature 3 in the valve housing 6 in an opening of the armature 3.
  • the contour of the lid 41 is inexpensively manufactured by deep drawing of thin sheet.
  • the lid 41 is liquid-tightly attached to the section 5 by means of a welded connection.
  • valve seat plate 43 To prevent a short-circuit current between the longitudinally and transversely the block-shaped housing 11 in the direction of the valve receiving bore 30 penetrating valve ports 39 is in the embodiment of FIG. 2 between the bottom of the valve receiving bore 30 and arranged on the journal-shaped end of the cup-shaped portion 7 valve seat plate 43 an elastomeric ring seal 32 inserted. Between the valve seat plate 43 and a plate filter 44 pressed into it, there is a check valve 45 which releases a bypass opening 48 in the valve seat plate 43, so that a connection between the valve connections 39 is possible independently of the position of the valve closure member 14.
  • FIG. 3 shows, based on the hydraulic valve according to FIG. 1, a hydraulic valve designed as a two-stage valve and closed in its basic position. It differs from Figure 1 in that the valve seat 8 is not arranged in the valve seat sleeve 26 of the section 7, but on a liftable valve piston 28 which is disposed within an axially movable driver 18 which is slidably guided for Magnetankerzentritation on the circumference of the valve seat sleeve 26 , In order to keep the overall height as low as possible, the carrier designed as a stepped sleeve 18 and the hub 18 of the valve piston 28 arranged in the liftably extends partially sunk in the already known from Figure 1 blind bore 37 of the armature 3.
  • valve piston 28 is thus preceded by the valve closing member 14 in series, which is not rigidly connected to the armature 3, unlike the hydraulic valve of Figure 1, but arranged as a plunger within the through hole relatively movable to the armature 3 and guided in a cap 38 adjacent to the through hole is that has a pressure compensation bore 35.
  • the cap 38 is fastened to the upper side of the magnet armature 3, on which the compression spring 17 inserted in the blind bore 16 in the section 5 is supported.
  • valve closure member 14 which is analogous 3 also extends to the bore 33 in Figure 2 on the valve seat 8, which is now part of the axially movable in the armature 3 valve piston 28.
  • valve piston 28 closes in the electromagnetically non-energized magnet armature under the action of the compression spring 17 another disposed in the valve seat sleeve 26 valve seat 29, which has a significantly larger valve seat surface relative to the valve seat 8.
  • the arranged between the driver 18 and the shaft end of the valve piston 28 compression spring 19 is dimensioned such that when electromagnetic excitation of the armature 3 of the valve piston 28 can remain on the valve closing member 14, as long as the valve piston 28 is not hydraulically pressure balanced.
  • the valve closing member 14 acts as a pilot stage and only relative to the effective as a main stage large valve seat 29 a relatively small throttle area 40 within the valve piston 28 free, so that the volume flow is largely determined by the hydraulically initiated position of the valve piston 28, including the valve piston 28 from the valve seat 29th is lifted off.
  • the magnet armature 3 is guided on the one hand by the driver 18 on the valve seat sleeve 26, on the other hand by a directed into the radial gap 4 annular disc 49 precisely in the valve housing 6.
  • the annular disc 49 is for this purpose inserted between the magnetic coil 1 and the section 7.
  • non-electromagnetically excited Ven- til too take due to the closing force of the compression spring 17 whose spring force is larger than the force of the oppositely acting compression spring 19, both valve closing body (valve closure member 14, 28) their valve closing positions.
  • the push-type valve closing member 14 bears against the end wall on the inner wall of the cap 38 and presses the sleeve-shaped valve closing member 28 onto the valve seat 29.
  • the illustrated hydraulic valves are preferably used in a slip-controlled brake system, there are generally no constant hydraulic pressures in the pressure medium inlet (horizontal valve connection 39 ) and Druckschauslass (vertical valve port 39) before, wherein the pressure in the pressure medium inlet usually predominates.
  • the magnet armature 3 initially compresses the compression spring 17 until the abutment of the tappet stage 46 mounted on the valve arm 4 on the armature 3 returns a partial lift X1. During this partial stroke thus the hydraulically not pressure-balanced valve closing member 14 remains under the action of the hydraulic pressure in the illustrated closed position on the valve piston 28.
  • valve piston 28 is also supported by the compression spring 19 and the sleeve-shaped driver 18 to open the throttle-free large cross section on the valve seat 29 can.
  • a hydraulic pressure equalization is established within the valve housing 6, which facilitates the lifting of the valve closure member 28 from the valve seat 29.
  • valve closing member 28 takes place as soon as the end face of the armature 3 rigidly connected driver 18 contacts the collar 50 of the hollow piston-shaped valve closure member 38, wherein the compression spring 19, the valve closing member 28 on the forced by the driver 18 stroke of the valve seat 29 in addition so that it is able to lift completely as soon as the hydraulic pressure equalization has taken place via the throttle cross-section 40.
  • the advantage of the telescopic arrangement of the two valve closing members 14, 28 in the armature 3 is thus that in a electromagnetically initiated lifting movement of the armature 3 is initially covered until the armature 3 at the plunger stage of the valve closing member 14 is already a partial stroke of the armature 3, the required for opening the valve closing member 28 stroke and thus also significantly reduced by the magnetic field to be bridged axial gap 2, so that after the pressure equalization over the Throttle bore 40 with a relatively low magnetic force designed for a large volume flow rate valve closure member 28 via the driver 18 from the valve seat 29 can be lifted accordingly.
  • the presented hydraulic valves are preferably used in a slip-controlled motor vehicle brake system, for which the valve block 11 shown only in sections has a plurality of valve receiving bores 30, which are shown in several rows for receiving the illustrated two-stage valve and the illustrated normally closed and normally open hydraulic valves in the valve block 11 are admitted.
  • the illustrated hydraulic valves in this case fulfill the function of selectively influencing the Bremstikauf- and the brake pressure reduction in the wheel brakes in the slip rule by means of a suitable control electronics, which preferably rests directly flat and thus extremely compact on the top of the hydraulic valves.
  • the result of the proposed features according to the invention is a particularly short hydraulic valve in various embodiments with a comparison with the previously known valves increased magnetic force, since the radial gap 4 is particularly small due to the valve design described.
  • the inventively proposed hydraulic valves can be completely submerged as needed in the valve block 11, which is ensured by the complete integration of the solenoid coil 1 in the valve housing 6 and due to the extensive integration capacity of the valve housing 6 in the channel-guiding valve block 11 excellent heat dissipation for the magnetic drive.
  • the complete integration of the hydraulic valves in the block-shaped housing 11 not only facilitates the arrangement of a control electronics required for the activation of the hydraulic valves, which is preferably arranged directly on the surface of the section 5, from which the contacts 23 of the magnetic coil 1 protrude, but ensures a Good heat dissipation for the control electronics, as the section 5 and the valve block preferably made of a light metal alloy 11 act as a heat sink or large-sized cooling surface.

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

Abstract

L'invention concerne une soupape hydraulique avec un boîtier de soupape (6) qui reçoit un organe de fermeture de soupape (14) coopérant avec une armature d'aimant (3), cet organe de fermeture de soupape étant orienté vers un siège de soupape (8) dans le boîtier de soupape (6), avec une bobine magnétique (1) pour l'actionnement de l'armature d'aimant (3), qui est connectée fixement à une partie (5) du boîtier de soupape (6) conduisant le flux magnétique, la bobine magnétique (1) étant directement adjacente à l'armature d'aimant (3) pour réduire la résistance magnétique, de sorte que la bobine magnétique (1) est exposée à un liquide pouvant être introduit et évacué par le biais des canaux de fluide sous pression (9, 10) dans le boîtier de soupape (6).
PCT/EP2006/068593 2005-11-19 2006-11-17 Soupape hydraulique WO2007057438A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102005055228.5 2005-11-19
DE102005055228 2005-11-19
DE102006004101.1 2006-01-28
DE102006004101A DE102006004101A1 (de) 2005-11-19 2006-01-28 Hydraulikventil

Publications (1)

Publication Number Publication Date
WO2007057438A1 true WO2007057438A1 (fr) 2007-05-24

Family

ID=37635864

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/068593 WO2007057438A1 (fr) 2005-11-19 2006-11-17 Soupape hydraulique

Country Status (2)

Country Link
DE (1) DE102006004101A1 (fr)
WO (1) WO2007057438A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009041446A1 (de) * 2009-09-16 2011-03-24 Svm Schultz Verwaltungs-Gmbh & Co. Kg Elektromagnet
DE102010002284A1 (de) * 2010-02-24 2011-08-25 Continental Teves AG & Co. OHG, 60488 Ventilanordnung, insbesondere für schlupfgeregelte Kraftfahrzeug-Bremsanlagen

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1650574A1 (de) * 1967-11-15 1970-09-10 Teldix Gmbh Elektromagnetisch betaetigbares Miniaturventil mit Tauchankermagnetsystem
DE8914152U1 (de) * 1989-12-01 1990-02-08 Pierburg GmbH, 4040 Neuss Elektromagnetisches Mehrwegeventil
DE10254342A1 (de) * 2002-05-02 2003-11-13 Continental Teves Ag & Co Ohg Elektromagnetventil
EP1124714B1 (fr) * 1998-10-28 2004-01-21 Robert Bosch Gmbh Dispositif electromagnetique, notamment destine a un systeme de freinage hydraulique et anti-patinage d'un vehicule

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4001938C3 (de) * 1990-01-24 2001-07-19 Mannesmann Ag Lineareinheit
DE19537659A1 (de) * 1995-10-10 1997-04-17 Teves Gmbh Alfred Ventilanordnung, insbesondere Elektromagnetventilanordnung für schlupfgeregelte Kraftfahrzeugbremsanlagen

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1650574A1 (de) * 1967-11-15 1970-09-10 Teldix Gmbh Elektromagnetisch betaetigbares Miniaturventil mit Tauchankermagnetsystem
DE8914152U1 (de) * 1989-12-01 1990-02-08 Pierburg GmbH, 4040 Neuss Elektromagnetisches Mehrwegeventil
EP1124714B1 (fr) * 1998-10-28 2004-01-21 Robert Bosch Gmbh Dispositif electromagnetique, notamment destine a un systeme de freinage hydraulique et anti-patinage d'un vehicule
DE10254342A1 (de) * 2002-05-02 2003-11-13 Continental Teves Ag & Co Ohg Elektromagnetventil

Also Published As

Publication number Publication date
DE102006004101A1 (de) 2007-05-24

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