EP0898531A1 - Soupape d'arret a commande hydraulique et systeme de freinage hydraulique de vehicule - Google Patents

Soupape d'arret a commande hydraulique et systeme de freinage hydraulique de vehicule

Info

Publication number
EP0898531A1
EP0898531A1 EP98902944A EP98902944A EP0898531A1 EP 0898531 A1 EP0898531 A1 EP 0898531A1 EP 98902944 A EP98902944 A EP 98902944A EP 98902944 A EP98902944 A EP 98902944A EP 0898531 A1 EP0898531 A1 EP 0898531A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
shut
actuating element
brake cylinder
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.)
Withdrawn
Application number
EP98902944A
Other languages
German (de)
English (en)
Inventor
Norbert Alaze
Heinz Siegel
Rolf Hummel
Thomas Michl
Martin Maier
Günther HOHL
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
Priority claimed from DE19732988A external-priority patent/DE19732988A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0898531A1 publication Critical patent/EP0898531A1/fr
Withdrawn legal-status Critical Current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
    • B60T8/48—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 connecting the brake actuator to an alternative or additional source of fluid pressure, e.g. traction control systems
    • B60T8/4809—Traction control, stability control, using both the wheel brakes and other automatic braking systems
    • B60T8/4827—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems
    • B60T8/4863—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems
    • B60T8/4872—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems pump-back 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
    • B60T8/341—Systems characterised by their valves
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7835—Valve seating in direction of flow

Definitions

  • the invention relates to a hydraulically actuated shut-off valve with the features of the preamble of claim 1 and to a hydraulic vehicle brake system that can be equipped with such a shut-off valve with the features of the preamble of claim 7.
  • Such a valve is known from EP 0 606 840 B1.
  • the known valve has a valve housing with an intermediate wall on which a valve seat is formed.
  • a piston is arranged as an actuating element on one side of the intermediate wall, said piston being pressed in the direction of the intermediate wall by a valve opening spring and being displaceable away from the intermediate wall by pressurization.
  • On the other side of the intermediate wall there is a valve ball as a valve closing body, which is lifted off the valve seat by the piston and is pressed in the direction of the valve seat by a valve closing spring which is weaker than the valve opening spring.
  • the well-known valve is in opened in its basic position and is closed by applying a pressure that is above a closing pressure.
  • the known valve has the disadvantage that its production is complex.
  • the valve housing must be machined on both sides of the valve seat. It is large and requires two springs that are matched to one another to set the desired switching pressures. By using two springs working against each other, there is a great risk that the switching pressures will change in the course of valve use.
  • This valve is part of a hydraulic vehicle brake system which is set up to limit drive slip by automatically braking drive wheels and for this purpose has at least one self-priming feed pump which is supplied with brake fluid from the reservoir by the open valve and by a master brake cylinder.
  • the hydraulic vehicle brake system also contains pressure build-up and pressure relief valve arrangements connected to wheel brake cylinders, by means of which brake fluid delivered by the feed pump for generating brake pressure, for example in traction control mode, can be supplied to at least one wheel brake cylinder.
  • the shut-off valve according to the invention with the features of claim 1 has only three moving parts, namely the valve closing body, the actuating element and a rocker element which transmits a movement of the actuating element to the valve closing body.
  • the geometry of these parts is simple and therefore inexpensive to manufacture. They can be accommodated in a cylindrical bore, which can have a cone on a ring step as a valve seat.
  • the shut-off valve according to the invention can be produced inexpensively with little effort, it is maintenance-free and is subject to only slight wear, so that it has a long service life.
  • the shut-off valve according to the invention is intended in particular for use as an intake valve for a hydraulic vehicle brake system having a pump, that is to say, for example, an anti-lock device, a traction slip device, a vehicle dynamics control device and / or an external vehicle brake system.
  • the shut-off valve is interposed between a master brake cylinder and a suction side of the pump, it is preferably open in its basic position and has a large flow cross-section in order to throttle as little as possible a brake fluid flow sucked in from a reservoir through the master brake cylinder when the master brake cylinder is not activated and thereby ensure a quick build-up of pressure.
  • the shut-off valve Due to the pressure build-up when the master brake cylinder is actuated, the shut-off valve is closed that the suction side of the pump is hydraulically separated from the master cylinder and brake fluid from wheel brake cylinders through a brake pressure reduction valve during an anti-lock control system or the like. can flow freely.
  • Driving dynamics control operation and / or power brake operation with the brake pedal actuated.
  • the characterizing features of claim 10 result in an embodiment which is more advantageous for driving dynamics control operation and / or power brake operation.
  • the configuration according to the characterizing feature of claim 11 results in an inexpensive design.
  • FIG. 1 shows an axial section of a shut-off valve according to the invention
  • Figure 2 is a hydraulic circuit diagram of a vehicle brake system according to the invention.
  • Figure 3 shows another hydraulic circuit diagram of a vehicle brake system according to the invention.
  • the hydraulically actuated shut-off valve according to the invention shown in FIG. 1, designated overall by 10, is a 2/2-way valve. It is inserted into a hydraulic block, of which only a fragment containing the shut-off valve 10 is shown in the drawing.
  • the shut-off valve 10 is hydraulically connected to other components of a vehicle brake system, such as solenoid valves, a master brake cylinder or a pump, via the hydraulic block.
  • the hydraulic block forms a valve housing 12 and is referred to below in this way.
  • the valve housing 12 has a cylindrical bore which forms a valve chamber 14. At the bottom of the valve chamber 14 there is an annular step with a conical valve seat 16, on which an axial fluid channel 18 opens.
  • a spherical valve closing body 20 is axially displaceably mounted in the valve chamber 14. This has longitudinal ribs 22 on its circumference. The longitudinal ribs 22 serve for the axial guidance of the valve closing body 20 in the valve chamber 14 and enable an almost unrestricted flow around the valve closing body 20.
  • valve closing body 20 is in one piece with a valve tappet 24 which is arranged axially in the valve chamber 14 and projects from the valve closing body 20 on a side facing away from the valve seat 16.
  • the valve lifter 24 projects through an annular actuating element 26 with an essentially rectangular ring cross section, which is located on one of the valve seats 16 facing end of the valve chamber 14 is located.
  • the actuating element 26 fills a space between the valve tappet 24 and a wall of the valve chambers 14, it has a clearance fit both with the valve tappet 24 and with the wall of the valve chamber 14. As a result, it guides the valve tappet 24 in the axial direction and is itself axially displaceably guided in the valve chamber 14.
  • a sleeve sealing ring 28 is arranged on an end face of the actuating element 26 which faces the valve seat 16 and which seals between the wall of the valve chamber 14 and the valve tappet 24.
  • sleeve sealing ring 28 it is also possible, for example, to provide a seal between the outer circumference of the actuating element 26 and the wall of the valve chamber 14 and a seal between the inner circumference of the actuating element 26 and the valve tappet 24 (not shown).
  • These seals are e.g. B. in grooves of the actuator 26 inserted sealing rings, preferably O-rings.
  • the valve chamber 14 is closed by means of a sealing plug 30 inserted into its mouth and caulked in a fluid-tight manner.
  • a rocker element 34 in the form of a plate spring is arranged between the sealing plug 30 and the actuating element 26. With slits running inwards from the outer circumference and / or outwards from the inner circumference, the elasticity of the seesaw element 34 can be influenced.
  • the rocker element 34 engages in a groove 36 of the valve stem 24.
  • the actuating element 26 is close to one Outer circumference on the rocker element 34.
  • the rocker element 34 5 lies on a circular edge which is formed by a cup-shaped recess 38 on an end face of the closure plug 30 facing the rocker element 34.
  • the annular edge forms a pivot bearing 40 for the rocker element 34.
  • a radial, second fluid channel 42 opens into the valve chamber 14 in the area between the sleeve seal 28 and the valve closing body 20.
  • the valve seat 16 is therefore located between the two fluid channels 18, 42.
  • shut-off valve 10 The function of the shut-off valve according to the invention is as follows: In a basic position of the shut-off valve 10 according to the invention shown in the left half of FIG. 1, the rocker element 34 designed as a disk spring lifts the valve closing body 20 from the valve seat 16, so that the shut-off valve 10 can be flowed through in both directions.
  • the embodiment shown in the drawing of a shut-off valve 10 according to the invention is therefore open in its basic position.
  • the rocker element 34 designed as a plate spring is elastically flattened by the actuating element 26, its outer edge moving in the direction of the sealing plug 30 and an inner edge which engages with the groove 36 of the valve tappet 24 in the direction of the valve seat 16. If the pressure in the valve chamber 14 drops below the switching pressure determined by the elastic spring force of the rocker element 34, the spring force of the rocker element 34 returns the shut-off valve 10 to its open basic position.
  • the shut-off valve 10 (FIG. 1) is provided according to the invention for use as a hydraulically actuated intake valve 44 in the vehicle brake system shown in FIG. 2.
  • FIG. 2 shows a brake circuit I of a two-circuit vehicle brake system 46.
  • the brake circuit II is constructed in accordance with the brake circuit I shown and functions in the same way.
  • the vehicle brake system 46 has a tandem master brake cylinder 48 with a reservoir 50.
  • a branching main brake line 52 leads from the main brake cylinder 48 to wheel brake cylinder 54 connected to this brake circuit I.
  • a changeover valve 56 which is open in its basic position, with an integrated pressure relief valve 58 is switched on.
  • a pressure build-up valve 60 which is open in its basic position is connected upstream of each wheel brake cylinder 54.
  • each wheel brake cylinder 54 has a pressure reduction valve 62 which is closed in its basic position, from which a common return line 64 leads to the main brake line 52 and opens between the changeover valve 56 and the pressure build-up valves 60.
  • a feed pump 66 is switched on, a storage 68 upstream and a damper 70 are connected downstream.
  • the pressure build-up and the pressure reduction valve 60, 62 form a brake pressure modulation valve arrangement of the respective wheel brake cylinder 54, with which the brake pressure in the wheel brake cylinder 54 can be modulated in a manner known per se in order to slip the corresponding vehicle wheel when braking (anti-lock control) when starting
  • the brake pressure modulation takes place with the aid of the feed pump 66.
  • the changeover valve 56 can be closed during the brake pressure modulation in order to have repercussions to prevent the master cylinder 48.
  • Pressure build-up and pressure reduction valves 60, 62 can, for example, also be combined to form a 3/3 valve instead of the separate 2/2 valves shown.
  • An intake line 72 leads from the master brake cylinder 48 to a suction side of the feed pump 66.
  • An intake valve 74 which is closed in its basic position is arranged in the intake line 72. Through the intake line 72, the feed pump 66 sucks brake fluid directly from the master brake cylinder 48 when the intake valve 74 is open, which is a prerequisite for rapid pressure build-up.
  • the suction valve 74 like the changeover valve 56 and the pressure build-up and pressure reduction valves 60, 62, is designed as a solenoid valve.
  • a flow cross section of the intake valve 74 is limited for design reasons; the intake valve 74 represents a throttle point when brake fluid is drawn in from the master brake cylinder 48 with the feed pump 66.
  • the hydraulically actuated shutoff valve 10 (FIG. 1) ) as an additional suction valve 44 (FIG. 2) connected in parallel to the suction valve 74, which is designed as a solenoid valve.
  • the flow resistance during the intake of brake fluid from the master brake cylinder 48 by means of the feed pump 66 is thereby further reduced and the pressure build-up is accelerated. Since the hydraulically actuated intake valve 44 has a constructional design, it is considerably easier larger flow cross-section than the electromagnetically operated suction valve 74 allows, the suction resistance can be significantly reduced with little effort.
  • the additional intake valve 44 is open in its basic position, so that the feed pump 66 can draw from the reservoir 50 when the master brake cylinder 48 is not actuated. If the master cylinder 48 is actuated, the valve chamber 14 of the shut-off valve 10 (FIG. 1) is pressurized via the intake line 72 and closed, i.e. H. the additional suction valve 44 ( Figure 2) switches automatically hydraulically controlled and does not need to be controlled electrically.
  • the hydraulically actuated, additional suction valve 44 can also replace the suction valve 74 designed as a solenoid valve in embodiments of the invention.
  • the axial fluid channel 18 shown in FIG. 1 connects the intake valve 44 to the low-pressure side of the feed pump 66 in the application example shown in FIG. 2.
  • the second fluid channel 42 opening radially into the valve chamber 14 (FIG. 1) connects the master brake cylinder 48 in the application example according to FIG with the intake valve 44.
  • the intake valve 44 shown symbolically in FIG. 2 can be designed according to the invention like the shut-off valve 10 shown in FIG.
  • the additional intake valve can also deviate from the Figure 1 be formed and selected for example from the prior art.
  • intake valves or at least intake valve elements according to the publications WO 94/29149 and WO 97/10132 or alternatively, for example, a copy of the intake valve 74 designed as a solenoid valve, which is represented by symbols in the alternative hydraulic circuit diagram of FIG. 3 at reference numeral 44a.
  • the dual-circuit vehicle brake system of FIG. 3 is given the reference symbol 46a.
  • a copy of the suction valve 74 can be carried out, for example, on a scale of 1: 1 in the sense of identical construction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

L'invention concerne une soupape d'arrêt à commande hydraulique (10) servant de soupape d'amorçage montée entre un maître-cylindre de frein et un côté aspiration d'une pompe d'alimentation d'un système de freinage de véhicule à antiblocage. Selon l'invention, la soupape d'arrêt (10) est pourvue d'un corps d'obturation (20) présentant un poussoir de soupape (24). Ce corps d'obturation traverse un élément d'actionnement annulaire (26) et vient coopérer avec un élément basculant (34) se présentant sous la forme d'une rondelle conique qui prend appui sur un palier pivotant annulaire (40). Lorsque l'élément d'actionnement (26) est soumis à une pression, il abaisse un bord extérieur de l'élément basculant (34). Une moitié de l'élément d'actionnement (26) exécute alors un mouvement de pivot en sens inverse qui provoque la fermeture de la soupape d'arrêt (10). Cette soupape d'arrêt (10) est peu onéreuse, présente un nombre restreint de composants et peut être utilisée dans un système de freinage hydraulique de véhicule. L'invention concerne également un système de freinage hydraulique de véhicule, comportant un maître-cylindre de frein (48), des cylindres de frein sur roue (54) alimentés en pression de freinage par ledit maître-cylindre (48), des ensembles soupape de montée en pression et soupape de réduction de pression (60, 62) affectés aux cylindres de frein sur roue, une pompe d'alimentation à amorçage automatique (66) pour chaque circuit de freinage, une soupape d'amorçage (74) montée entre le maître-cylindre de frein et une entrée (64) de la pompe d'alimentation (66) qui est raccordée aux ensembles soupape de montée en pression et soupape de réduction de pression (60, 62), et une soupape de commutation (56) montée entre une sortie de la pompe d'alimentation (66) et le maître-cylindre (48). Ce système de freinage hydraulique de véhicule est caractérisé en ce qu'une deuxième soupape d'amorçage est montée en parallèle avec la soupape d'amorçage (74). Ce système de freinage permet un meilleur remplissage de la pompe d'alimentation (66).
EP98902944A 1997-03-13 1998-01-09 Soupape d'arret a commande hydraulique et systeme de freinage hydraulique de vehicule Withdrawn EP0898531A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19710426 1997-03-13
DE19710426 1997-03-13
DE19732988A DE19732988A1 (de) 1997-03-13 1997-07-31 Hydraulisch betätigbares Absperrventil und hydraulische Fahrzeugbremsanlage
DE19732988 1997-07-31
PCT/DE1998/000054 WO1998040257A1 (fr) 1997-03-13 1998-01-09 Soupape d'arret a commande hydraulique et systeme de freinage hydraulique de vehicule

Publications (1)

Publication Number Publication Date
EP0898531A1 true EP0898531A1 (fr) 1999-03-03

Family

ID=26034825

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98902944A Withdrawn EP0898531A1 (fr) 1997-03-13 1998-01-09 Soupape d'arret a commande hydraulique et systeme de freinage hydraulique de vehicule

Country Status (4)

Country Link
US (1) US6189984B1 (fr)
EP (1) EP0898531A1 (fr)
JP (1) JP2000511491A (fr)
WO (1) WO1998040257A1 (fr)

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Publication number Priority date Publication date Assignee Title
US7819740B2 (en) * 2003-02-10 2010-10-26 Igt Gaming device having a plurality of paylines and different modifiers associated with the paylines
DE10327567B4 (de) * 2003-06-18 2014-07-10 Robert Bosch Gmbh Verfahren zur Betätigung einer Fremdkraft-Feststellbremsanlage
DE10327571B4 (de) * 2003-06-18 2016-05-12 Robert Bosch Gmbh Verfahren zur Betätigung einer Fremdkraft-Feststellbremsanlage
DE102011089956A1 (de) * 2011-12-27 2013-06-27 Robert Bosch Gmbh Hydraulisch gesteuertes Speicherkammerventil
DE102014107599B9 (de) * 2014-05-28 2016-01-21 Eto Magnetic Gmbh Regelbare Magnetventilvorrichtung und Verwendung einer solchen
US10472923B2 (en) * 2014-11-05 2019-11-12 M-I L.L.C. Trim for choke

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DE2262247A1 (de) * 1972-12-20 1974-06-27 Teves Gmbh Alfred Elektromagnetisches ventil
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JPH0655909U (ja) 1993-01-14 1994-08-02 住友電気工業株式会社 ブレーキ液圧制御装置
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JP2895770B2 (ja) * 1995-04-05 1999-05-24 日本エービーエス株式会社 アンチスキッド液圧制御装置
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GB9518073D0 (en) * 1995-09-05 1995-11-08 Pressure Wise Ltd Valves with reverse buckling discs
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DE19537926B4 (de) * 1995-10-12 2004-04-15 Continental Teves Ag & Co. Ohg Verfahren zum Betrieb einer hydraulischen Bremsanlage
JPH11509501A (ja) * 1996-05-14 1999-08-24 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング 液圧式の車両ブレーキ装置

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Also Published As

Publication number Publication date
US6189984B1 (en) 2001-02-20
WO1998040257A1 (fr) 1998-09-17
JP2000511491A (ja) 2000-09-05

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