WO2006077179A1 - Soupape a commande electrique - Google Patents

Soupape a commande electrique Download PDF

Info

Publication number
WO2006077179A1
WO2006077179A1 PCT/EP2006/050065 EP2006050065W WO2006077179A1 WO 2006077179 A1 WO2006077179 A1 WO 2006077179A1 EP 2006050065 W EP2006050065 W EP 2006050065W WO 2006077179 A1 WO2006077179 A1 WO 2006077179A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
valve control
piston
spool
pressure
Prior art date
Application number
PCT/EP2006/050065
Other languages
German (de)
English (en)
Inventor
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
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2006077179A1 publication Critical patent/WO2006077179A1/fr

Links

Classifications

    • 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
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F16F9/466—Throttling control, i.e. regulation of flow passage geometry

Definitions

  • the invention relates to an electrically controllable valve, in particular for use in an adjustable shock absorber, according to the preamble of patent claim 1.
  • valves for use in a shock absorber are known. These valves form a valve assembly consisting of a pre-stage and a main-stage valve.
  • a solenoid is provided, which is connected for the variable adjustment of a valve opening cross-section in the valve housing with a valve piston whose valve sealing surfaces cooperate with a valve seat in the valve housing.
  • the object of the invention is to design a valve, in particular for use in a shock absorber, with as little effort as possible in such a way that a pressure-regulating and pressure-limiting function is ensured by using as simple as possible, functionally reliable means.
  • Fig. 1 is a longitudinal section through a valve with the characteristics underlying the invention in a first pressure control position in which the excitation current corresponds to the maximum electrical drive current imax of the valve spool for actuating a valve spool, whereby the desired fluid flow flows through the valve under high fluid pressure, including a first valve opening cross-section Vl closed, an aperture Sl and a second valve opening cross-section V2 arranged upstream thereof is released,
  • FIG. 2 shows the valve of Figure 1 in a further pressure control position, in which the excitation current corresponds to the minimum electrical drive current imin, whereby the desired fluid flow flows through the valve under low fluid pressure, including due to an intermediate position of the valve spool both valve port cross sections Vl, V2 are partially released,
  • FIG. 4 shows a characteristic field for clarification of the valve switching positions shown in FIG. 1-3 resulting fluid flows,
  • Fig. 5-12 the individual manufacturing steps for the valve.
  • FIG. 1 shows the Fig. 1 in longitudinal section an electrically actuated, monodirectionally operated valve, which is preferably used for controlling a shock absorber in a motor vehicle.
  • the valve consists of an electric actuator 1, consisting of a designed in plunger type armature 13 and a valve spool 5.
  • the armature 13 is connected via a comparativelyiförmigen extension 7 with the valve spool 2.
  • the valve control piston 2 has substantially the contour of a valve spool, which is alternately applied with its lateral surface on two aligned in series with each other in the valve housing 4 valve control edges 3, 3 '.
  • the two valve control edges 3, 3 ' are formed by two transverse bores within a bushing 6 inserted in the valve housing 4, which are closed or released by two piston edges of the valve control piston 2.
  • the valve control piston 2 in the region of the first valve control edge 3 on its circumference a groove-shaped circumferential recess 15, while the second piston edge on the valve spool 2 is formed by a recess 15 'in the form of a V-shaped annular groove on the height of the second valve control edge 3 'and in the bushing 6 below the second valve control edge 3' provided inlet channel 11 extends.
  • the latter recess 15 ' is advantageously carried out so deep in the valve spool 2 that the fluid flow when passing through the inlet channel 11 is able to act hydraulically on a precisely defined in diameter, in the piston longitudinal direction in the recess 15 'extending insert body 8.
  • valve control piston 2 has a first and a second piston section 2 a, 2 b, which are both connected to one another by the piston shaft in the region of a groove-shaped constriction 21.
  • the two insert bodies 8 guided through the first piston section 2a of the valve control piston 2 can also be acted upon hydraulically in the desired manner.
  • the two piston portions 2a, 2b provided with through holes.
  • the insert body 8 are supported with their protruding from the valve spool 2 ends of stops 12, which are spaced from the two end faces of the valve spool 2 in the valve housing 4 and. are fixed to the bushing 6.
  • the insert body 8 are preferably designed as metallic sealed in the through-holes cylindrical pins which remain under hydraulic application to the stops 12, while the valve spool 2 moves for the purpose of hydraulic pressure limiting or pressure control relative to the insert bodies 8.
  • the inlet channel 11 penetrates as a transverse bore below the second valve control edge 3 ', the bushing 6. Between the inlet channel 11 and the second valve control edge 3', the bushing 6 a likewise as a transverse bore the bushing 6 penetrating aperture bore S2. Downstream of the second valve control edge 3 ', the first valve control edge 3 as well as the (first) diaphragm aperture S1 are in the form of a transverse bore in the bushing 6. At the lower end of the bush 6 is closed with a decker-shaped stop 12, on which the inserted into the lower piston portion 2b insert body 8 is supported.
  • An outlet channel 10 is located downstream of the first valve control edge 3 and downstream of the first diaphragm opening Sl above the bushing 6 in the valve housing 4.
  • valve control piston 2 is designed as well as the armature 13 as precisely guided in the valve housing 4 plunger.
  • the extension 7 and the armature 13 integral valve assembly has a through hole 14 which extends longitudinally in the valve assembly extends.
  • a compression spring 9 in order to position the valve spool 2 in the electrically de-energized state at the second valve control edge 3 'can.
  • the sealing effect between the valve control edges 3, 3 'and the valve seat body 2 is produced exclusively by edge covering.
  • two variably adjustable valve opening cross-sections V 1, V 2 in the region of the bushing 6, with which a controlled fluid flow passes, are produced with electromagnetic excitation of the actuator 1.
  • variable second valve opening cross section V2 is located upstream of the first valve opening cross section Vl in a series connection to the first valve opening cross section Vl, wherein both valve opening cross sections Vl, V2 are reciprocally open in proportion to one another by means of the valve control piston 2. to be closed.
  • the aperture cross-section is smaller than a provided in the region of the second valve opening cross section V2 aperture S2.
  • the apertures Sl, S2 are introduced as bores in the longitudinal and transverse direction in the bushing 6.
  • the pressure increase p can be limited in a desired manner when the valve control piston 2 is attached to the first or second valve control edge 3, 3 'as a function of the volume flow Q (range I of the characteristic diagram depicted in FIG. 4).
  • the hydraulic applied surfaces of the valve spool 2 are interpreted differently taking into account the spring and magnetic force, which is why the hydraulically actuated piston surface A3 of the valve spool 2 in the region of the inlet channel 11th smaller than the piston area A2 of the valve control piston 2 in the region of the second valve control edge 3 'is to be dimensioned, on the other hand j edoch, however, the piston area A3 is greater than the piston area Al in the region of the first valve control edge third
  • the hydraulically actuated piston surfaces A1, A2, A3 are of the diameter designed to influence the piston surfaces Al, A2, A3 fixed insert bodies 8 penetrated.
  • A3 ( ⁇ / 4) (d4 2 ) where Al ⁇ A3 ⁇ A2.
  • the subject invention is advantageously designed such that an axial working air gap XA of the electric actuator 1 is disposed on the side facing away from the valve spool 2 side of a cooperating with the valve spool 2 armature 13, so that upon electrical actuation of the actuator 1, the valve spool 2 from the rest position at the second valve control edge 3 'in the direction of the first valve control edge 3 is movable.
  • valve control piston 2 is hydraulically not pressure balanced due to the realized by the insert body 8 different active surfaces Al, A2, A3, so that taking into account the between the valve spool 2 and the Actuator 1 arranged compression spring 9, the map shown in Figure 4 comes about.
  • the hydraulic flow forces that occur during the flow through the valve are at least partially compensated by the sketched body geometry of the valve control piston 2 in the region of the two recesses 15, 15 '.
  • FIG. 1 shows the valve with the features on which the invention is based in a first pressure control position, in which the excitation current corresponds to the maximum electrical drive current of the valve coil 5 mounted on the valve housing 4.
  • the armature 13 holds the valve spool 2 against the action of the return spring 9 in register at the first valve control edge 3, so that initially passes exclusively through the aperture Sl, the fluid flow at high pressure p from the inlet channel 11 to the outlet channel 10.
  • the pressure medium thus passes from below into a first annular space 16 provided between the bushing 6 and the valve housing 4 and extending to the inlet channel 11.
  • the pressure medium enters the V-shaped recess 15 ', where it is guided by the contour of the recess 15' in the direction of the unlocked second valve. til torturekante 3 'advantageously deflected, after which the pressure medium again passes into a separate from the first annulus 16 second annulus 17, which allows a hydraulic connection to the first valve control edge 3 and the same in the bushing 6 arranged first aperture Sl. Since the valve control piston 2 with its lateral surface holds the first valve control edge 3 closed, the pressure medium passes exclusively via the first diaphragm opening Sl to the outlet channel 10, resulting in the characteristic curve profile shown in FIG.
  • FIG. 2 shows the valve in a control position in which the exciter current corresponds to the minimum electrical drive current of the valve coil 12.
  • the armature 13 moves the valve spool 2 against the action of the compression spring 9 in a stable intermediate position in which both valve control edges 3, 3 'and thus their flow cross-sections Vl, V2 are released to a maximum flow between the inlet and Outlet channel 11, 10 to allow.
  • FIG. 4 illustrated pressure control characteristic imin, from which a shallow pressure increase with increasing volume flow Q can be seen.
  • valve control piston 2 closes due to the action of the compression spring 9, first, the second valve control edge 3 ', whereby the second valve opening V2 is virtually blocked up to the fluid flow through the aperture S2.
  • the steep characteristic curve progression in region I shown in FIG. 4 initially results.
  • any set of curves by any number of positions of the valve spool 2 represent, of which explicitly three characteristic curves were exemplified with reference to Figures 1-3.
  • the ordinate of the diagram shows in each case the pressure rise p and along the abscissa the volumetric flow Q is plotted.
  • FIG. 5 firstly shows the valve housing 4 designed as a deep-drawn sleeve, in which the annular disk-shaped stop 12, which is likewise designed as a deep-drawn part, is inserted from below and is preferably pressed into a narrowed step section of the valve housing 4. From the top to the extended step portion of the valve housing 4, a retaining ring 18 is slipped over the valve sleeve 4, which serves to receive the provided for the magnetic drive 13 yoke ring. The retaining ring 18 is laser-welded to the valve housing 4 and the upper stop 12 in the region of the upper step portion.
  • FIG. 6 shows the valve control piston 2, which is already equipped with the two insert bodies 8 in the piston section 2a and is inserted with the bushing 6 from below with an assembly tool 22 into the valve housing 4.
  • FIG. 7 shows the next assembly step, according to which the magnet armature 13 is pressed onto the extension 7 from above into the valve housing 4 until the top stop 12 contacts.
  • the case effective reaction force is absorbed by the mounting tool 22.
  • FIG. 8 shows the subsequent assembly of the compression spring 9 and the magnetic core 19 from above into the valve housing 4, wherein for adjusting the valve lift a mandrel 20 presses through the hole in the mounting tool 22 against the underside of the valve spool 2, before the magnetic core 19th is finally positioned in the valve sleeve 4 and welded.
  • Figure 9 shows the subsequent adjustment of the biasing force of the compression spring 9 by the spring force is measured during the displacement of an acting in the magnetic core 19 on the compression spring 9 adjusting sleeve 20 acting from below against the valve spool 2 setting mandrel.
  • the assembly tool 22 is removed and inserted according to Figure 10 from below into the initially free passage opening of the valve spool 2 of the insert body 8 and secured against falling out by the ceiling-shaped stop 12 on the bushing 6.
  • FIG. 11 shows the placement of the valve spool 5 with the yoke ring on the valve housing 4 until the yoke ring at the bottom of the retaining ring 18 rests. This is followed, finally, by welding of the yoke ring in the region of the collar on the retaining ring 18, to which reference is made to FIG.
  • valve control edge 3 valve control edge

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne une soupape à commande électrique dont l'entrefer de travail axial (XA) est placé sur la face, opposée au piston de commande de soupape (2), d'un induit magnétique (13) coopérant avec le piston de commande de soupape (2) de sorte que, en cas d'actionnement électrique du servomoteur (1), le piston de commande de soupape (2) peut être déplacé par le servomoteur (1) en direction de la première arête de commande de soupape (3). Selon l'invention, on obtient un état du piston de commande de soupape (2) non équilibré en pression hydrauliquement au moyen de plusieurs inserts (8).
PCT/EP2006/050065 2005-01-21 2006-01-06 Soupape a commande electrique WO2006077179A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102005002912 2005-01-21
DE102005002912.4 2005-01-21
DE102005023547.6 2005-05-21
DE102005023547A DE102005023547A1 (de) 2005-01-21 2005-05-21 Elektrisch ansteuerbares Ventil

Publications (1)

Publication Number Publication Date
WO2006077179A1 true WO2006077179A1 (fr) 2006-07-27

Family

ID=36202561

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/050065 WO2006077179A1 (fr) 2005-01-21 2006-01-06 Soupape a commande electrique

Country Status (2)

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DE (1) DE102005023547A1 (fr)
WO (1) WO2006077179A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111108303A (zh) * 2017-12-01 2020-05-05 大众汽车有限公司 用于布置在减振装置内的能电控的阀的接触装置

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007023716A1 (de) 2006-11-02 2008-05-08 Continental Teves Ag & Co. Ohg Proportionalregelventil
DE102009019552A1 (de) * 2009-04-30 2010-11-11 Hydac Fluidtechnik Gmbh Proportional-Drosselventil
DE102012111882B4 (de) * 2012-12-06 2017-06-29 Thyssenkrupp Ag Elektromagnetisches Proportionalventil
LU102984B1 (de) * 2022-07-27 2024-01-29 Thyssen Krupp Bilstein Gmbh Dämpfungsventileinrichtung für einen Schwingungsdämpfer
WO2024022922A1 (fr) * 2022-07-27 2024-02-01 Thyssenkrupp Bilstein Gmbh Dispositif de soupape d'amortissement pour amortisseur de vibrations
WO2024022925A1 (fr) * 2022-07-27 2024-02-01 Thyssenkrupp Bilstein Gmbh Dispositif de soupape d'amortissement pour amortisseur de vibrations
LU102988B1 (de) * 2022-07-27 2024-01-29 Thyssenkrupp Ag Dämpfungsventileinrichtung für einen Schwingungsdämpfer
WO2024022915A1 (fr) * 2022-07-27 2024-02-01 Thyssenkrupp Bilstein Gmbh Dispositif de soupape d'amortissement pour amortisseur de vibrations
LU102987B1 (de) * 2022-07-27 2024-01-29 Thyssenkrupp Ag Dämpfungsventileinrichtung für einen Schwingungsdämpfer

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19624898A1 (de) 1996-06-21 1998-01-02 Mannesmann Sachs Ag Dämpfventil mit veränderbarer Dämpfkraft
WO2001036243A1 (fr) * 1999-11-16 2001-05-25 Continental Teves Ag & Co. Ohg Vanne electromagnetique
FR2805492A1 (fr) * 2000-02-28 2001-08-31 Peugeot Citroen Automobiles Sa Systeme de regulation pour une suspension de vehicule automobile
WO2006008272A1 (fr) * 2004-07-19 2006-01-26 Continental Teves Ag & Co. Ohg Soupape a commande electrique

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3813402C2 (de) * 1988-04-21 1998-04-09 Stabilus Gmbh Dämpfventile mit geschwindigkeitsabhängig wirkender - stark progressiver Dämpfkraft
DE3917064A1 (de) * 1989-05-26 1990-11-29 Bosch Gmbh Robert Stossdaempfer ii
DE4129581C2 (de) * 1991-09-06 2000-10-05 Continental Teves Ag & Co Ohg Steuerbare Ventilanordnung für regelbare Zweirohr-Schwingungsdämpfer
DE4423526C1 (de) * 1994-03-03 1995-12-07 Fichtel & Sachs Ag Schwingungsdämpfer mit verstellbarer Dämpfkraft
DE19531010B4 (de) * 1995-08-23 2004-04-29 Robert Bosch Gmbh Magnetventil, insbesondere für eine schlupfgeregelte, hydraulische Bremsanlage für Kraftfahrzeuge
DE10139222B4 (de) * 2001-08-09 2005-07-21 Zf Sachs Ag Schwingungsdäpfer mit verstellbarer Dämpfkraft

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19624898A1 (de) 1996-06-21 1998-01-02 Mannesmann Sachs Ag Dämpfventil mit veränderbarer Dämpfkraft
WO2001036243A1 (fr) * 1999-11-16 2001-05-25 Continental Teves Ag & Co. Ohg Vanne electromagnetique
FR2805492A1 (fr) * 2000-02-28 2001-08-31 Peugeot Citroen Automobiles Sa Systeme de regulation pour une suspension de vehicule automobile
WO2006008272A1 (fr) * 2004-07-19 2006-01-26 Continental Teves Ag & Co. Ohg Soupape a commande electrique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111108303A (zh) * 2017-12-01 2020-05-05 大众汽车有限公司 用于布置在减振装置内的能电控的阀的接触装置
CN111108303B (zh) * 2017-12-01 2021-12-03 大众汽车有限公司 用于布置在减振装置内的能电控的阀的接触装置

Also Published As

Publication number Publication date
DE102005023547A1 (de) 2006-07-27

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