EP0785885A1 - Vanne electromagnetique a limitation de pression pour systemes de freinage d'automobiles a regulation antipatinage - Google Patents

Vanne electromagnetique a limitation de pression pour systemes de freinage d'automobiles a regulation antipatinage

Info

Publication number
EP0785885A1
EP0785885A1 EP95934045A EP95934045A EP0785885A1 EP 0785885 A1 EP0785885 A1 EP 0785885A1 EP 95934045 A EP95934045 A EP 95934045A EP 95934045 A EP95934045 A EP 95934045A EP 0785885 A1 EP0785885 A1 EP 0785885A1
Authority
EP
European Patent Office
Prior art keywords
valve
seat
pressure
sleeve
tappet
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
EP95934045A
Other languages
German (de)
English (en)
Inventor
Martin Oehler
Günther HOHL
Hans-Peter Huebner
Norbert Mittwollen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0785885A1 publication Critical patent/EP0785885A1/fr
Ceased legal-status Critical Current

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
    • 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
    • B60T8/365—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems combining a plurality of functions in one unit, e.g. pressure relief
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S303/00—Fluid-pressure and analogous brake systems
    • Y10S303/90—ABS throttle control
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S303/00—Fluid-pressure and analogous brake systems
    • Y10S303/901—ABS check valve detail

Definitions

  • the invention relates to a solenoid valve according to the preamble of the patent claim.
  • Such a solenoid valve is already known (DE 42 34 749 AI), which is arranged in slip-controlled brake systems of motor vehicles in a brake line between a master brake cylinder and the pressure side of a high-pressure pump conveying into the brake line, as described in the document DE 40 41 506 AI is.
  • the solenoid valve With traction control, the solenoid valve is switched to its closed position and the pressure limiting function is activated. If the pump pressure exceeds the opening pressure of the valve, its seat valve goes into the partially open position against the force of the pressure limiting spring, so that pressure medium can flow out to the master brake cylinder. Because of the pulsating pump, pressure surges occur in the downstream brake line part, which can cause disturbing noises in the motor vehicle interior. But that is particularly annoying Pressure surge that occurs when the valve is switched off from the closed position to the open position.
  • the solenoid valve according to the invention with the characterizing features of the claim has the advantage that a pressure medium flow into the gap space is caused by the shape of the valve seat, closing member and sleeve-shaped portion of the outer valve lifter part during the transition of the seat valve from the closed position to the partially open position, which creates a dynamic pressure there caused, which is transmitted through the pressure medium channel into the control chamber and exerts a force on the magnet armature, which counteracts the hydraulic opening force and thus greatly slows the opening process of the seat valve into the open position.
  • the volume flow of the pressure medium through the seat valve can only increase in a throttled manner, so that at most a very reduced pressure surge becomes effective in the downstream brake line part. This greatly improves the noise behavior of the brake system when the solenoid valve is switched off. But even with effective pressure limitation, considerable noise reduction is achieved through flow stabilization as a result of a defined flow guidance.
  • FIG. 1 shows a longitudinal section through a solenoid valve
  • FIGS. 2 and 3 flow curves in the seat valve area designated X in FIG. 1 of the valve which assumes its open position (FIG. 2) and its partially open position (FIG. 3).
  • the solenoid valve 10 with pressure limitation shown in Figure 1 is intended for use in slip-controlled brake systems of motor vehicles.
  • the solenoid valve 10 has a valve housing 11 which is intended to be received in a valve block (not shown) and which is connected to a yoke disk 12.
  • the valve housing 11 is continued beyond the yoke plate 12 with a pole core 13.
  • a closed, tubular valve dome 14 is attached to the pole core 13. This is tightly connected to the pole core 13 by welding.
  • the valve dome 14 facing away from the pole core is closed with a hemispherical cap 15.
  • the valve dome 14 is encompassed by an annular magnet coil 18.
  • a bell-shaped housing 19 engages the valve dome 14 on the one hand, and it is connected to the yoke disk 12 on the other hand.
  • valve dome 14 which is closed on the coil side, an essentially circular cylindrical magnet armature 22 is accommodated in a longitudinally movable manner.
  • a valve tappet 23 is supported on the magnet armature 22.
  • the magnet armature 22 and the valve tappet 23 are separate components which engage one another in a sealing seat 24.
  • the valve tappet 23 has a tubular, outer valve tappet part 25, in which a second, inner valve tappet part 26 is guided so as to be longitudinally movable.
  • a press-in sleeve 27 is seated in the outer valve-tappet part 25.
  • a pressure-limiting spring 28 in the form of a helical compression spring is located in the valve tappet 23 between the press-in sleeve 27 of the outer valve tappet part 25 and the inner valve tappet part 26. This engages with prestress on the one hand on the press-in sleeve 27 and on the other hand on a collar 29 of the inner valve lifter part 26, which in turn is supported on a shoulder 30 of the outer valve lifter part 25.
  • valve stem 23 is received in a through bore 33 of the valve housing 11 so as to be longitudinally movable. Polkernabge andt a valve body 34 of a seat valve 35 is pressed into the housing bore 33.
  • the valve tappet 23 is supported on the magnet armature 22 by a return spring 36 acting on the one hand on the valve body 34 and on the other hand on the outer valve tappet part 25.
  • the valve body 34, the parts 25 and 26 of the valve stem 23 and the magnet armature 22 are arranged in the longitudinal axis 37 of the solenoid valve 10.
  • the seat valve 35 is located in the region of a valve chamber 40 which has the bore 33 with a transverse bore 41 of the valve housing 11 forms.
  • the seat valve 35 has a valve seat 43 formed in the valve body 34 and enclosing a valve opening 42 in a hollow cone shape (FIGS. 2 and 3).
  • the valve seat 43 is located in a straight, circular-cylindrical recess 44 in the valve body 34.
  • the recess 44 is delimited against the valve chamber 40 by a sharp edge 45 by an end face 46 of the valve body 34 running at right angles to the longitudinal axis 37 of the valve.
  • valve chamber 40 While the valve chamber 40 is connected to a pressure medium inlet 47 through the transverse bore 41, the valve opening 42 is connected through the perforated valve body 34 to a pressure medium outlet 48 of the solenoid valve 10.
  • the pressure medium inlet 47 is connected to a master brake cylinder, the pressure medium outlet 48 with at least one wheel brake cylinder and the high pressure side of a return pump of the hydraulic brake system of the motor vehicle, not shown, for example known from DE 40 41 506 A1.
  • the seat valve 35 has a closing element 51 which interacts with the valve seat 43 and which is formed by a straight circular cylindrical section 52 of the inner valve lifter part 26 with a reduced diameter.
  • the section 52 merges into a spherical segment 54 of low height against the valve seat 43, forming a sharp edge 53.
  • the ball segment 54 assumes a position approximately in the region of the end face 46 of the valve body 34.
  • the section 52 of the inner valve lifter part 26 is encompassed by a sleeve-shaped section 57 of the outer valve lifter part 25.
  • the sleeve-shaped section 57 extends at a radial distance from the circular-cylindrical section 52, ie the inner lateral surface 58 of the sleeve-shaped section has one even distance from the circular cylindrical section.
  • a gap 59 is formed between the sleeve-shaped section 57 and the circular-cylindrical section 52, which is open towards the valve chamber 40.
  • the sleeve-shaped section 57 has an axial residue with respect to the ball segment 54.
  • the recess 44 has a diameter which is equal to or smaller than the inner diameter of the sleeve-shaped section 57, in the exemplary embodiment shown approximately between the latter and the section 52 of the inner valve lifter part 26.
  • the tangent 60 strikes the jacket wall 62 of the recess 44.
  • the sleeve-shaped section 57 has a considerably smaller axial distance from the end face 46 of the valve body 34 than in the open position.
  • a pressure medium channel 65 extending essentially in the longitudinal valve axis 37 extends from the gap space 59. Only on the inner valve tappet part 26 is the pressure medium channel 65 formed as at least one recess 66 following the circular cylindrical section 52 in the form of a longitudinal notch or groove. Following the recess 66, the pressure medium channel runs 65 in the interior of the outer valve lifter part 25 and the press-in sleeve 27 and, after the sealing seat 24, merges into a longitudinal bore 67 of the armature 22.
  • the pressure medium channel 65 opens into a control chamber 68 which is delimited on the one hand by the cap 15 and on the other hand by the end face 69 of the magnet armature 22 remote from the seat valve.
  • the control chamber 68 is sealed on the circumferential side of the armature 22 against the valve dome 14. For this purpose there is a sealing sleeve on the magnet armature
  • the armature 22 can also be sealed with a gap seal 72 against the valve dome.
  • the solenoid valve 10 has the following mode of operation:
  • the seat valve 35 When braking without slip control, the seat valve 35, which assumes its open position, is flowed through from the pressure medium inlet 47 to the pressure medium outlet 48 when pressure builds up in the wheel brake cylinders, and pressure medium flows in the opposite direction when the pressure is reduced.
  • the pressure medium takes a path through the seat valve 35 into the valve chamber 40, as is indicated by streamlines in FIG.
  • the pressure medium flowing through the valve seat 43 from the valve hope 42 is deflected approximately tangentially by the ball segment 54 of the closing element 51, the flow tearing off at the sharp edge 53 of the closing element 51.
  • the pressure medium leaves the recess 44 in the direction of the tangent 60 and partially meets the end face 61 of the sleeve-shaped section 57 of the outer valve lifter part 25. There, the pressure medium undergoes a radial deflection into the valve chamber 40, from which it flows out to the pressure medium inlet 47.
  • the collar 29 of the inner valve stem part 27 is overcome the biasing force of the pressure limiting spring 28 is raised from the shoulder 30 of the outer valve lifter part 25. While the force flow of the pressure limiting spring 28 was previously closed via the collar 29 of the inner valve tappet part 26, the outer valve tappet part 25 and the press-in sleeve 27, at the end of the armature stroke, the pressure limiting spring 28 exerts an axial force on the inner valve tappet part 26, with which this means by means of its closing member 51 engages the valve seat 43 of the valve body 34. The force of the pressure limiting spring 28 now acts as the closing force of the seat valve 35 which determines the opening pressure of the solenoid valve 10.
  • the solenoid valve 10 When the closing member 51 engages the valve seat 43, the solenoid valve 10 thus functions as a shut-off valve with a pressure-limiting effect on the part of the brake system on the side of the brake cylinder. If the opening pressure of the solenoid valve 10 is exceeded by the return pump, the pressure limiting function becomes effective. The closing member 51 lifts against the force of the pressure limiting spring 28 from the valve seat 43 and takes it A partially open position of the seat valve 35 shown in FIG. 3.
  • the streamlines take a course corresponding to the tangent 60 when penetrating the narrow gap between the valve seat 43 and the ball segment 54 and meet the casing wall 62 of the recess 44 when leaving the valve seat.
  • the streamlines experience an axial deflection so that they partly when leaving the recess 44 penetrate into the gap 59 between the closing member 51 and the sleeve-shaped section 57 and generate a dynamic pressure there, which also acts on the circumferential side on the circular cylindrical section 52 of the closing member 51.
  • This defined flow control suppresses possible instabilities of the present jet flow, so that the closing member 31 is not subjected to changing impulse forces and is therefore not excited to vibrate.
  • the dynamic pressure is also transmitted through the pressure medium channel 65 into the control chamber 68, where it causes a hydraulic force directed against the seat valve 35 on the magnet armature 22.
  • this force has no effect on the seat valve 35.
  • the pressure medium flow is directed out of the gap space 59, so that the pressure medium takes a radial path between the two end faces 46 and 61 of the valve body 34 and the sleeve-shaped section 57 in the direction of the pressure medium inlet 47.

Landscapes

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

Abstract

L'invention vise à mettre au point une vanne électromagnétique qui produise peu de bruit lors de l'arrêt de la fonction de limitation de pression. Cette vanne électromagnétique (10) comporte un poussoir (23) en deux parties, dont la partie intérieure (26) présente l'élément de fermeture (51) d'une soupape à siège (35). L'élément de fermeture (51) est entouré par une section (57) de type manchon de la partie extérieure (25) du poussoir, à distance de ladite section (57), ce qui forme un espace (59) d'où part un canal de fluide hydraulique (65) qui mène jusqu'à une chambre de commande (68). Cette dernière (68) se trouve entre la face d'about (69), éloignée de la soupape à siège, d'un noyau magnétique (22) qui coopère avec le poussoir (23) et un dôme de soupape (14). Lorsque la vanne électromagnétique (10) est arrêtée, la soupape à siège (35) passe d'une position fermée dans une position semi-ouverte, dans laquelle de la pression de retenue intervient dans l'espace (59) et est transférée à travers le canal de fluide hydraulique (65) dans la chambre de commande (68). La force hydraulique qui s'exerce là sur le noyau magnétique (22) agit à l'encontre les forces d'ouverture de la vanne électromagnétique (10) et ralentit son mouvement d'ouverture. Il en résulte une réduction de l'écoulement de fluide hydraulique à travers la soupape à siège (35), ce qui permet d'éviter des phénomènes de coups de bélier. Cette vanne électromagnétique (10) s'utilise dans des systèmes de freinage pour automobiles, à régulation antipatinage.
EP95934045A 1994-10-27 1995-10-10 Vanne electromagnetique a limitation de pression pour systemes de freinage d'automobiles a regulation antipatinage Ceased EP0785885A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4438336 1994-10-27
DE4438336A DE4438336A1 (de) 1994-10-27 1994-10-27 Magnetventil mit Druckbegrenzung für schlupfgeregelte Kraftfahrzeug-Bremsanlagen
PCT/DE1995/001386 WO1996013414A1 (fr) 1994-10-27 1995-10-10 Vanne electromagnetique a limitation de pression pour systemes de freinage d'automobiles a regulation antipatinage

Publications (1)

Publication Number Publication Date
EP0785885A1 true EP0785885A1 (fr) 1997-07-30

Family

ID=6531801

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95934045A Ceased EP0785885A1 (fr) 1994-10-27 1995-10-10 Vanne electromagnetique a limitation de pression pour systemes de freinage d'automobiles a regulation antipatinage

Country Status (6)

Country Link
US (1) US6086164A (fr)
EP (1) EP0785885A1 (fr)
JP (1) JPH10507813A (fr)
KR (1) KR970706997A (fr)
DE (1) DE4438336A1 (fr)
WO (1) WO1996013414A1 (fr)

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DE19805404A1 (de) * 1998-02-11 1999-08-12 Itt Mfg Enterprises Inc Drucksteuerventil
DE19815778A1 (de) * 1998-04-08 1999-10-14 Bosch Gmbh Robert Absperrventil mit Druckbegrenzungsfunktion, insbesondere für schlupfgeregelte hydraulische Bremsanlagen von Kraftfahrzeugen
US6412884B1 (en) * 1998-09-30 2002-07-02 Tokico Ltd. Solenoid-controlled valve
DE19956821A1 (de) * 1998-11-30 2000-05-31 Denso Corp Elektromagnetisches Ventil für die Bremshydraulikdruck-Steuerung und Fahrzeugbremssteuersystem hiermit
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US6431207B1 (en) * 2000-03-16 2002-08-13 Ross Operating Valve Company High-pressure ball-poppet control valve
EP1167148B1 (fr) * 2000-07-01 2008-02-06 Robert Bosch GmbH Méthode et appareil de calcul de l'actionnement d'un sous-ensemble hydraulique FDR/ESP afin de réduire des bruits hydrauliques
US6634722B1 (en) * 2001-07-31 2003-10-21 Kelsey-Hayes Company Vehicle braking system with proportional poppet valve pressure control strategy
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DE10321413B4 (de) * 2003-05-13 2014-06-26 Robert Bosch Gmbh Elektromagnetisch betätigbares Ventil
JP4010982B2 (ja) * 2003-06-03 2007-11-21 日信工業株式会社 電磁弁
DE102004001565A1 (de) * 2004-01-10 2005-08-04 Robert Bosch Gmbh Elektromagnetisches Ventil, insbesondere für eine Bremsanlage eines Kraftfahrzeugs
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DE102005057674B4 (de) * 2005-12-01 2008-05-08 Alstom Technology Ltd. Abhitzekessel
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DE102008014192B4 (de) * 2008-03-14 2014-04-10 Hilite Germany Gmbh Antriebsstrang mit einem Fahrdynamiksystem und elektrohydraulischem Ventil
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DE102010002602A1 (de) * 2010-03-05 2011-09-08 Robert Bosch Gmbh Magnetventil zum Steuern eines Fluids
DE102014101437A1 (de) * 2014-02-05 2015-08-06 Eto Magnetic Gmbh Elektromagnetventil sowie Verbrennungsmotorkühlsystem mit Elektromagnetventil
DE102014225323A1 (de) * 2014-12-09 2016-06-09 Robert Bosch Gmbh Schalt- oder Druckregelventil für ein Karftstoffeinspritzsystem

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Also Published As

Publication number Publication date
JPH10507813A (ja) 1998-07-28
DE4438336A1 (de) 1996-05-02
WO1996013414A1 (fr) 1996-05-09
KR970706997A (ko) 1997-12-01
US6086164A (en) 2000-07-11

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