WO2001014196A1 - Soupape a action continue - Google Patents

Soupape a action continue Download PDF

Info

Publication number
WO2001014196A1
WO2001014196A1 PCT/EP2000/008180 EP0008180W WO0114196A1 WO 2001014196 A1 WO2001014196 A1 WO 2001014196A1 EP 0008180 W EP0008180 W EP 0008180W WO 0114196 A1 WO0114196 A1 WO 0114196A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
closing body
valve closing
continuous
seat
Prior art date
Application number
PCT/EP2000/008180
Other languages
German (de)
English (en)
Inventor
Ulrich Neumann
Stefan A. Drumm
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 DE10007349A external-priority patent/DE10007349A1/de
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2001014196A1 publication Critical patent/WO2001014196A1/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
    • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
    • B60T15/02—Application and release valves
    • B60T15/025—Electrically controlled valves
    • B60T15/028—Electrically controlled valves in hydraulic 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
    • B60T8/50—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F15B13/0442—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors with proportional solenoid allowing stable intermediate positions

Definitions

  • the invention relates to a continuous valve, in particular for electrohydraulic brake systems, according to the preamble of patent claim 1.
  • DE 196 04 315 AI has already disclosed such an electromagnetically actuated continuous valve, which is designed as a seat valve, with a funnel-shaped valve seat and a closing body in the form of a spherical segment.
  • An inflow hole connected to a pressure medium outlet m opens centrally into the valve seat.
  • a plunger which has the closing body is engaged by a magnetic armature which acts on the poppet valve and a restoring spring which acts on the valve.
  • the seat valve which is basically designed as a 2/2-way valve, can be operated as an analog switching valve due to the selected sealing diameter on the valve seat and the selected cone angle on the valve seat, as well as the continuously variable magnetic force, taking into account the spring and hydraulic forces acting on the closing body.
  • the object is achieved in that the fixed orifice previously arranged in the flow direction in front of the valve closing body is now arranged behind the valve closing body which acts as a variable orifice.
  • This measure increases the local hydraulic pressure at the valve closing body, which means that the vapor pressure limit is theoretically not exceeded until very high flow speeds, which cannot be achieved if the valve is designed accordingly.
  • a turbulence generator preferably a sieve or a filter or the like, is positioned upstream of the valve closing body, so that the most uniform possible turbulent flow in the direction of flow through the valve closing body while maintaining the lowest possible pressure loss and the valve seat body formed variable aperture cross section.
  • valve closing body can have both an axial or a radial sealing surface with the function of a seat or slide valve, so that the invention is not limited to the exemplary embodiment shown below.
  • FIG. 1 shows a valve assembly consisting of a solenoid valve inserted into a valve receiving body 3, the valve housing 7 of which accommodates a movably arranged valve closing body 11, which is connected to an actuating device 12 designed as a magnetic drive.
  • This solenoid valve is designed as a so-called continuous valve, i.e. with a flow cross-section that can be opened or closed in the sense of a variable orifice function, in which the valve closing body 11 is located, the position of the valve closing body 11 within a defined valve stroke by means of the electromechanical actuating device 12 during the Valve flow is stabilized in such a way that the stroke of the valve closing body 11 always remains constant during the electrical valve actuation.
  • valve seat body 5 has a funnel-shaped valve seat surface on the tappet side with a funnel angle of at most 110 degrees.
  • the valve seat pool ends radially outward with sharp edges on an end face 9, which delimits the valve seat body 5 against a valve chamber 10.
  • the valve chamber 10 is connected to a transverse bore 15 m, which forms the pressure medium outlet of the continuous valve.
  • this transverse bore 15 there is the fixed orifice 22 arranged downstream of the valve seat body 5.
  • the magnet armature 16 and the plunger are also flushed with pressure medium via the valve chamber 10.
  • the valve closing body 11 has the shape of a Kuge1 segment.
  • the valve closing body 11 is attached on the end face to a cylindrical section of the tappet.
  • the funnel angle of the valve seat and the radius of the valve closing body 11 are coordinated with one another in such a way that the sealing diameter of the valve seat is at least 1.3 times the diameter of the inflow bore 21.
  • the diameter of the tappet corresponds at least approximately to the sealing diameter of the valve seat, i.e. the tappet is slightly larger than the sealing diameter.
  • the transition of the valve closing body 11 to the tappet is formed with sharp edges.
  • valve seat of the valve seat body 5 and the valve closing body 11 on the tappet form a seat valve which assumes its open position due to the action of the return spring 14 when the solenoid 19 is not energized.
  • the electromagnetically actuated continuous valve is therefore in principle a switching valve in the form of a 2/2-way valve. It can be used in hydraulic brake systems of motor vehicles.
  • valve according to the invention differs from the known 2/2 directional control valves in the following way:
  • the inflow-side pressure acts on an effective area dependent on the sealing diameter. before the plunger and exerts an opening force on the plunger.
  • the downstream pressure in the valve chamber 10 and in the valve dome is lower than the upstream pressure and acts with a force to close the tappet.
  • the hydraulic force resulting from these two forces thus has an opening effect on the tappet, as does the return spring 14 designed as a helical compression spring.
  • valve closing body 11 and the valve seat body 5 ensure that the analog valve actuation is largely free of interference flows. A small deflection of the pressure medium flow in the seat valve is achieved by the selected funnel angle of the valve seat. As a result, few impulse forces are generated, which occur especially with large flows. The dependency of the valve properties on the differential pressure and temperature of the pressure medium is therefore low. Furthermore, the sharp-edged transition between the valve closing body 11 and the tappet ensures that the pressure medium flow always breaks off there and thus leads to uniform flow forces on the valve closing body 11. The sharp-edged outlet of the valve seat on the end face 9 of the valve seat body 5 also contributes to a stable flow of pressure medium.
  • the resulting hydraulic force and spring force mentioned above is the result of energizing the magnetic Coil 19 generated, acting in the closing direction of the seat valve magnetic force opposed.
  • the magnetic force over the valve opening stroke also produces a monotonically falling course.
  • the amount is less than the sum of the resulting hydraulic force and the spring force.
  • Changed excitation currents can be set using current control, pulse-free modulation and other known methods.
  • the seat valve assumes a stable position at a defined stroke, which corresponds to the working point.
  • a magnetic force characteristic shifted by current control sets the operating point to a new valve opening stroke.
  • the continuous valve can thus be actuated steplessly, depending on the current, with a variable opening stroke.
  • the continuous valve according to the invention can be used in m electrohydraulic brake systems, so that with this valve it is advantageously possible to control the pressure and volume flow continuously.
  • a turbulence generator designed as a filter element 6 ′ is provided upstream of the valve closing body 11, which promotes the flow around the valve closing body 11 without causing a significant pressure drop.
  • the filter element 6 ′ which is also designed as a turbulence generator, is thus located immediately upstream of the valve seat body 11 m from the pressure medium inlet channel 17.
  • the essentially block-shaped valve receptacle body 3 has a stepped valve receptacle opening 2, which extends the valve housing 7 by way of example with a thin-walled sleeve 1 that extends with the valve closing body 11 corresponds to the corresponding valve seat body 5.
  • the diameter of the end region of the thin-walled sleeve 1 is matched to the valve receptacle opening 2, which is reduced inward, with a slight radial interference fit, so that a seal between the sleeve 1 and the valve receptacle body 3 is easily achieved.
  • the sleeve 1 is designed as a stepped sleeve which carries the valve seat body 5 in its enlarged inner area on the step 4.
  • Filter elements 6, 6 1 are arranged in the area of stage 4 and on the adjoining expanded section of the sleeve 1.
  • this relates, inter alia, to a filter element 6 which is designed as an Rmg filter and which is both on the outer circumference of the sleeve 1 in the area of the step 4 is also preferably held frictionally on the reduced outer diameter of the sleeve 1.
  • FIG. 1 which, like the valve seat body 5, is depicted in FIG the expanded area of the sleeve 1 is inserted at the bottom with the plate check valve 13 m and bears in sections on the underside of the valve seat body 5.
  • the thin-walled sleeve In order to securely fix the section of the thin-walled sleeve 1 directed towards the valve housing 7 to the valve housing 7, the thin-walled sleeve is adapted in its outer diameter to the opening 8 of the valve housing 7 and is pressed there. Because the opening 8 is designed as a stepped bore, it forms an axial abutment surface of the valve housing 7 for the sleeve 1, so that when the sleeve 1 is pressed in, the valve receiving opening 2 causes the resulting frictional force via the thin-walled sleeve m to be relatively stiff and thick-walled designed valve housing 7 initiated and thus can be received by the valve housing 7.
  • the return spring 14 holding the valve closing body 11 in the open position is supported on an annular surface of the sleeve 1, with which the sleeve 1 forms a spring stop and, if necessary, an additional centering and thus a guiding function by means of a correspondingly small tolerated through-opening for the tappet of the valve closing body 11 the valve closing body 11 takes over the valve seat body 5.
  • valve housing 7 there is also a dome-like, in the end region on its cylindrical shaft closed sleeve 18, which preferably closes the valve housing 7 in a pressure-tight manner by means of laser beam welding, the magnet armature 16 being arranged inside the dome-shaped closed sleeve 18 and the magnet coil 19 being arranged outside it.
  • the proposed invention is not limited to the exemplary embodiment shown in FIG. 1, but can also be used independently of the design as a seat valve for slide valves, since slide valves as well as seat valves in the area of the control edges are exposed to the phenomenon of cavitation , which can lead to unstable operation of the valve and to premature wear or damage to the valve seat and slide surfaces.

Landscapes

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

Abstract

L'invention concerne une soupape à action continue, en particulier pour système de freinage électrohydraulique, comprenant une section d'écoulement pouvant s'ouvrir ou se fermer à la manière du fonctionnement variable d'un diaphragme, section dans laquelle se trouve un corps d'obturation de soupape (11), la position de celui-ci étant stabilisée, pour une course déterminée, au moyen d'un dispositif de commande électromécanique pendant une traversée d'un corps de soupape (7) logeant le corps d'obturation (11), de telle façon que durant la commande de la soupape, la course dudit corps d'obturation (11) soit constante, ainsi qu'un diaphragme fixe (22) monté à la suite du corps d'obturation (11) dans le corps de soupape (7), destiné à limiter le débit volumique maximum du fluide dans la soupape. En vue d'éviter la cavitation, le diaphragme fixe (22) est monté en aval du corps d'obturation (11).
PCT/EP2000/008180 1999-08-25 2000-08-22 Soupape a action continue WO2001014196A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19940260.4 1999-08-25
DE19940260 1999-08-25
DE10007349.2 2000-02-18
DE10007349A DE10007349A1 (de) 1999-08-25 2000-02-18 Stetigventil

Publications (1)

Publication Number Publication Date
WO2001014196A1 true WO2001014196A1 (fr) 2001-03-01

Family

ID=26004401

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2000/008180 WO2001014196A1 (fr) 1999-08-25 2000-08-22 Soupape a action continue

Country Status (1)

Country Link
WO (1) WO2001014196A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2397868A (en) * 2002-11-19 2004-08-04 Bosch Gmbh Robert Electronically actuated valve for use in hydraulic brake systems

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4332820A1 (de) * 1993-06-09 1995-03-30 Teves Gmbh Alfred Hydraulische Bremsanlage mit Schlupfregelung
US5647644A (en) * 1993-11-18 1997-07-15 Itt Automotive Europe Gmbh Solenoid valve, especially for hydraulic brake systems with slip control
DE19604315A1 (de) 1996-02-07 1997-08-14 Bosch Gmbh Robert Elektromagnetisch betätigtes Ventil, insbesondere für hydraulische Bremsanlagen von Kraftfahrzeugen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4332820A1 (de) * 1993-06-09 1995-03-30 Teves Gmbh Alfred Hydraulische Bremsanlage mit Schlupfregelung
US5647644A (en) * 1993-11-18 1997-07-15 Itt Automotive Europe Gmbh Solenoid valve, especially for hydraulic brake systems with slip control
DE19604315A1 (de) 1996-02-07 1997-08-14 Bosch Gmbh Robert Elektromagnetisch betätigtes Ventil, insbesondere für hydraulische Bremsanlagen von Kraftfahrzeugen

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2397868A (en) * 2002-11-19 2004-08-04 Bosch Gmbh Robert Electronically actuated valve for use in hydraulic brake systems
GB2397868B (en) * 2002-11-19 2005-03-02 Bosch Gmbh Robert Electromagnetically actuated valve, in particular for hydraulic brake systems in motor vehicles

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