WO2007014827A1 - Soupape hydraulique - Google Patents

Soupape hydraulique Download PDF

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Publication number
WO2007014827A1
WO2007014827A1 PCT/EP2006/064081 EP2006064081W WO2007014827A1 WO 2007014827 A1 WO2007014827 A1 WO 2007014827A1 EP 2006064081 W EP2006064081 W EP 2006064081W WO 2007014827 A1 WO2007014827 A1 WO 2007014827A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
armature
magnetic
housing
coil
Prior art date
Application number
PCT/EP2006/064081
Other languages
German (de)
English (en)
Inventor
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 WO2007014827A1 publication Critical patent/WO2007014827A1/fr

Links

Classifications

    • 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
    • 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
    • F16K31/0655—Lift valves
    • 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
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F16K31/0693—Pressure equilibration of the armature
    • 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
    • H01F7/081—Magnetic constructions

Definitions

  • the invention relates to a hydraulic valve according to the preamble of patent claim 1.
  • a non-ferromagnetic disc located below the magnetic coil, so that the magnetic flux via a disposed between the armature and the cylindrical valve housing section axial gap and between the armature and the valve housing existing radial gap in a desired manner to a closed magnetic circuit.
  • Figure 1 shows an embodiment of the subject invention in the form of a closed in basic position, two-stage
  • Figure 2 shows an embodiment of the subject invention in the form of a closed in the basic position, single-stage
  • 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 magnetic coil 1 is integrated directly in the valve housing 6, which is arranged in a magnetic flux conducting portion 5 of the valve housing 6 and fixedly connected to this section 5.
  • a variably adjustable by the armature stroke axial gap 2 is provided, which is bridged as well as provided between a lateral surface of the armature 3 and the valve housing 6 constant radial gap 4 during electromagnetic excitation of magnetic field lines.
  • the magnet coil 1 is therefore inventively designed as a plunger coil partially immersed in the pressure medium and the armature 3 as a stepped armature whose provided with a smaller diameter relative to the magnetic coil 1 center portion has a directed into a gap 20 of the magnetic coil 1 extension 21 which passes through the axial gap 2 of the end face of the valve housing 6 is spaced.
  • the extension 21 of the step armature is opposite to the extension 21 in diameter enlarged annular disc portion 22 which covers the end face of the magnetic coil 1 at an axial distance to the coil so far that the lateral surface of the annular disc portion 22 only by the radial gap 4 from the magnetically conductive portion 5 of the valve housing 6 is disconnected.
  • armature and coil design of the magnetic force loss is advantageously reduced with increasing armature stroke, so that if desired or demand with unchanged electrical energy demand relatively large armature strokes are possible.
  • valve housing 6 has a magnetic flux non-conductive further portion 7, which bears liquid-tight at the periphery of the magnetic portion 5, to which the further portion 7 is formed as a cup-shaped deep-drawn part, the valve seat 8 and two pressure medium channels 9, 10 receives in the lower region ,
  • 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.
  • the fixed by means of a self-caulking in the valve block 11, to the atmosphere as Einpressstopfen sealing portion 5 of the valve housing 6 is designed thick-walled for use in Hochdruckhydrauliksystemen and has for partially receiving the solenoid 1 adapted to the magnetic coil recess in which the magnetic coil 1 recorded accurately and securely fastened.
  • the protruding from the section 5 part of the magnetic coil 1 is of the fluid flowing through the valve housing 6 is applied directly, provided that 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 a.
  • valve housing 6 inserted in the form of a cartridge in the valve block 11 thus consists only of two cartridge halves, wherein the upper half of the housing is formed by the recess provided with the plug-shaped portion 5 and the lower half of the housing through the cup-shaped portion 7 which carries the valve seat 8.
  • 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 on all sides liquid-tight enclosed by a pressure-resistant housing, which forms the coil carrier.
  • the magnetic coil 1 is either fixed in the recess of the section 5 or fixed non-positively or positively via a pressure-resistant plastic sheath of the contact 23 in the through hole 13 of the valve housing 6.
  • 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.
  • the magnet armature 3 can also be produced in a simplified manner by extrusion or cold striking.
  • the hydraulic valves depicted in FIGS. 1 and 2 have a filter element 31 arranged on the pot-shaped section 7, which is embodied as a ring filter element and prevents dirt from entering the generally calibrated pressure medium channel 9.
  • the magnetic core is formed for each closed in the basic position hydraulic valves by the region of the directed into the magnetic coil 1 section 5, in the center of 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 valve base position of the Magnet armature 3 is held with the valve closing member 14 on the valve seat 8.
  • a sleeve-shaped guide member 29 is pressed into sections centrally from the bottom of the magnet armature 3, the sleeve end remote from the armature 3 is guided parallel to the valve seat body 35 pressed into the bottom of the cup-shaped section 7.
  • a plunger portion of the valve closure member 14 is also received telescopically slidably.
  • the valve closing member 14 extends with its tappet portion to a bore stage in the stepped bore 28, wherein the spring 19 is clamped between a collar 32 on the tappet portion and a stop fixed to the armature 3 stop 33, preferably a part of a fixedly connected to the armature 3 guide member 29 is. This results in a telescope-like interaction of armature and valve closure member to cover with minimal magnetic force required large armature strokes can.
  • the mentioned telescopic connection between the valve closing member 14 and the armature 3 has the advantage that at the beginning of electromagnetic excitation of the armature 3, the valve closing member 14 initially remains in the closed position on the valve seat 8 until the idle stroke (axial distance) between the collar 32 and the Driver 18 is completed as a result of the magnet armature. As soon as the driver 18 contacts the collar 32, the valve closing member 14 is lifted by its valve seat 8 and the pressure medium connection between the two pressure medium channels 9, 10 is released.
  • FIG. 1 shows a hydraulic valve designed as a two-stage valve and closed in the basic position.
  • valve closure member 14 of the plunger portion is designed as a sleeve with a throttle bore 36 which is closed by a further shock-shaped valve closure member 37 which is guided within a cap 38 which is fixed on the axial gap 2 facing end face of the armature 3 ,
  • the cap 38 is provided with a pressure equalization bore and extends between the spring coils of the compression spring 17 in the blind bore 16th
  • the further valve closing member 37 which is arranged in series with the valve closing member 14, closes in the electromagnetically non-excited magnet armature position under the action of the compression spring 17 a further valve seat 12 adjoining the throttle bore 36, which is thus a component of the sleeve-shaped valve closing member 14.
  • valve closing member 14 remains on the valve seat 8, as long as the valve closure member 14 is not hydraulically pressure balanced.
  • further valve closing member 37 acts as a pilot stage, by the Magnetankerhub positively controlled the throttle bore 36 releases pressure equalization.
  • non-energized solenoid valve position take due to the closing force of the compression spring 17 whose spring force is larger than the force of the oppositely acting spring 19, both arranged in series connection valve closure members 14, 37 their illustrated valve closing positions.
  • the push-type valve closure member 37 bears against the end wall on the inner wall of the cap 38 and presses the sleeve-shaped valve closure member 14 onto the valve seat 8.
  • 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 pressure medium outlet (vertical valve connection 34), wherein the pressure in the pressure medium inlet often predominates.
  • the armature 3 lays a partial stroke until the contacting of a step on the limit valve-shaped closing member 37.
  • the valve closing member 14 against the action of the spring 19 as a result of the hydraulic pressure first remains in the locked position until the meaning of Pilot stage via the throttle bore 36, a hydraulic pressure compensation takes place. Due to the hydraulic pressure compensation, the spring 19 can lift the valve closing 14 of the valve seat 8, whereby in the context of the main stage of the large passage cross-section between the valve closure member 14 and the valve seat 8 is opened.
  • the pressure fluid connection between the two valve ports 39, 41 is thus made resistant to resistance for a correspondingly large volume flow rate.
  • the advantage of the telescopic arrangement of the two valve closing members 14, 37 in the armature 3 is thus that in an electromagnetically initiated lifting movement of the armature 3 is initially covered until the armature 3 at the plunger stage of the valve closure member 37 is already a partial stroke of the armature 3, the considerably reduced to open the valve closing member 14 stroke and thus the magnetic field to be bridged axial gap 2, so that after pressure equalization via the throttle bore 36 with a relatively low magnetic force designed for a large volume flow rate valve member 14 via the driver 18 from the valve seat can be easily lifted accordingly.
  • the hydraulic valve of Figure 2 differs from the hydraulic valve of Figure 1 by the elimination of the elements of Vorordelcut, so that only necessary for the function of the main stage valve components are required, the known from Figure 1, essentially by the voltage applied in the basic position on the valve seat 8 valve closing member 14, the spring 19 and the driver 18 is formed.
  • valve closing member 14 is thus spring-loaded added in the stepped bore of the armature 3 in Figure 2. Due to the elimination of the pre-throttle stage, the valve closing member 14 in FIG. 2 has no throttle bore, so that the valve-closing member 14 has a closed Senen shaft portion which is supported by the already known from Figure 1 known spring 19 with its collar 32 in the stepped bore 28 of the magnet armature 3.
  • spring 19 and the driver 18 reference is made to FIG.
  • This further axial gap 26 is formed by a recess 24, which is arranged on the inner circumference of the magnetic section 5 and extends essentially in the shape of a groove, from the radial gap 4 spaced.
  • the recess 24 is to be understood as an example of a locally targeted cross-sectional weakening at the end portion of the section 5 (magnetic yoke). This cross-sectional weakening considerably reduces the leakage flux of the magnetic field in the transitional region between the radial gap 4 and the further axial gap 26 and thus contributes to an advantageous alignment or steering of the magnetic flux in the field line transition from the radial to the further axial gap 4, 26 during the magnetically initiated magnet armature stroke at.
  • the magnetic force effect with respect to the hydraulic valve of Figure 1 at a small axial gap 2 increases by at least 20 percent.
  • the electromagnetically initiated position of the magnet armature 3 with a small axial gap 2 can be seen from the right-hand half of the figure in FIG. In this position, the valve closing member 14 is located just before lifting from the valve seat 8 under exclusive axial magnetic force effect, since the annular disc portion 22 moves within the recess 24.
  • the left half of the picture illustrates the armature basic position in which both axial gaps 2, 26 represent a maximum in terms of magnitude.
  • the section 5 can be made in two parts as desired or required, which is shown by way of example in Figure 2, whereby the recess 24 and the housing projection 25 having lower part of the section 5 after assembly of the magnetic coil 1 in the upper part of the section. 5 can be joined easily with the top.
  • the presented hydraulic valves are preferably used in a slip-controlled 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 11th conceptually like the illustrated hydraulic valves. Ie can be executed. This results in a particularly compact braking device, the valve block 11 is particularly flat due to the low height of the illustrated hydraulic valves.
  • the illustrated hydraulic valves in this case fulfill the function of the suction side of a pump required for the brake pressure supply possible low resistance with a pressure medium source, preferably to be able to connect to the reservoir of a master cylinder.
  • the pump is electrically actuated for traction control or for automatic brake pressure control by means of a suitable control electronics, to which the control electronics preferably rests directly flat and thus extremely compact on the top of the hydraulic valves.

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

Abstract

L'invention concerne une soupape hydraulique comprenant un corps (6) dans lequel est logé un obturateur (14) qui coopère avec un induit magnétique (3) et qui est dirigé sur un siège (8) dans le corps (6), ainsi qu'une bobine magnétique (1) servant à actionner l'induit magnétique (3), cette bobine étant reliée de manière fixe à une section (5) du corps (6) conduisant le flux magnétique. Selon l'invention, pour réduire l'encombrement en hauteur de cette soupape et pour réduire la résistance magnétique, l'induit magnétique (3) est un induit à enroulement double dont la section centrale qui présente un diamètre inférieur à celui de la bobine magnétique (1) comprend un prolongement (21) dirigé dans un espace intermédiaire (20) de la bobine magnétique (1), ce prolongement (21) étant séparé de la surface frontale du corps (6) par l'interstice axial (2). La bobine magnétique (1) est disposée dans le corps (6) de la soupape sous la forme d'une bobine mobile autour de laquelle le liquide circule.
PCT/EP2006/064081 2005-08-04 2006-07-11 Soupape hydraulique WO2007014827A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102005037341.0 2005-08-04
DE102005037341 2005-08-04
DE102006001924.5 2006-01-14
DE102006001924A DE102006001924A1 (de) 2005-08-04 2006-01-14 Hydraulikventil

Publications (1)

Publication Number Publication Date
WO2007014827A1 true WO2007014827A1 (fr) 2007-02-08

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ID=36939260

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/064081 WO2007014827A1 (fr) 2005-08-04 2006-07-11 Soupape hydraulique

Country Status (2)

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DE (1) DE102006001924A1 (fr)
WO (1) WO2007014827A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007082816A1 (fr) * 2006-01-11 2007-07-26 Continental Teves Ag & Co. Ohg Soupape électromagnétique
US9620274B2 (en) 2015-02-17 2017-04-11 Enfield Technologies, Llc Proportional linear solenoid apparatus

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006027859B4 (de) * 2006-04-28 2015-05-21 Continental Teves Ag & Co. Ohg Elektromagnetventil
DE102008020101B4 (de) * 2008-04-22 2013-12-24 Staiger Gmbh & Co. Kg Ventil
DE102008039421B4 (de) * 2008-08-13 2012-03-22 Rolf Prettl Magnetventil und Verfahren zu dessen Herstellung
DE102015105116B4 (de) 2015-04-02 2019-09-19 Eto Magnetic Gmbh Elektromagnetventil sowie sicherheitsrelevantes Pneumatiksystem mit einem solchen Elektromagnetventil

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1273945B (de) * 1965-03-11 1968-07-25 Buehler Ag Geb Hydralischer Druckregler mit elektromagnetischem Stellglied
US4463332A (en) * 1983-02-23 1984-07-31 South Bend Controls, Inc. Adjustable, rectilinear motion proportional solenoid
DE19834303A1 (de) * 1998-07-30 2000-02-03 Lopic Michael Magnetventil
DE20001020U1 (de) * 2000-01-21 2001-06-07 Robert Bosch Gmbh, 70469 Stuttgart Elektromagnetisch betätigbares Druckregelventil
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
DE102004015661B4 (de) * 2004-03-31 2007-08-23 Bosch Rexroth Ag Elektropneumatisches Ventil, insbesondere Vorsteuerventil für ein pneumatisches Wegeventil
DE102004037269B3 (de) * 2004-07-31 2005-12-29 Bosch Rexroth Ag Elektropneumatisches Ventil mit pneumatisch betätigtem Steuerkolben

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1273945B (de) * 1965-03-11 1968-07-25 Buehler Ag Geb Hydralischer Druckregler mit elektromagnetischem Stellglied
US4463332A (en) * 1983-02-23 1984-07-31 South Bend Controls, Inc. Adjustable, rectilinear motion proportional solenoid
DE19834303A1 (de) * 1998-07-30 2000-02-03 Lopic Michael Magnetventil
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
DE20001020U1 (de) * 2000-01-21 2001-06-07 Robert Bosch Gmbh, 70469 Stuttgart Elektromagnetisch betätigbares Druckregelventil

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007082816A1 (fr) * 2006-01-11 2007-07-26 Continental Teves Ag & Co. Ohg Soupape électromagnétique
US9620274B2 (en) 2015-02-17 2017-04-11 Enfield Technologies, Llc Proportional linear solenoid apparatus
US9704636B2 (en) 2015-02-17 2017-07-11 Enfield Technologies, Llc Solenoid apparatus

Also Published As

Publication number Publication date
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