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WO1995011824A1 - Systeme de freinage hydraulique - Google Patents

Systeme de freinage hydraulique Download PDF

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Publication number
WO1995011824A1
WO1995011824A1 PCT/DE1994/001197 DE9401197W WO9511824A1 WO 1995011824 A1 WO1995011824 A1 WO 1995011824A1 DE 9401197 W DE9401197 W DE 9401197W WO 9511824 A1 WO9511824 A1 WO 9511824A1
Authority
WO
WIPO (PCT)
Prior art keywords
membrane
pressure
brake system
hydraulic brake
support wall
Prior art date
Application number
PCT/DE1994/001197
Other languages
German (de)
English (en)
Inventor
Klaus Mueller
Werner Wilde
Dietmar Baumann
Hans-Friedrich Schwarz
Hans-Peter Huebner
Norbert Mittwollen
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 WO1995011824A1 publication Critical patent/WO1995011824A1/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
    • B60T8/48—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
    • B60T8/36—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
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B60T8/368—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units combined with other mechanical components, e.g. pump units, master cylinders

Definitions

  • the invention relates to a hydraulic brake system according to the preamble of the main claim.
  • a hydraulic brake system is known (DE-A 41 28 386).
  • Such a known brake system has the peculiarity that it provides an additional pressure medium volume for the traction slip operation with relatively little constructive means without any control effort, while avoiding narrow cross-sections and short distances to the high-pressure pump.
  • the memory is only flexible in the filling direction of the system. Pressure peaks cannot be smoothed out by the accumulator because its hose membrane usually bears against a solid wall.
  • a shut-off valve and a pressure relief valve are used during traction control.
  • the pressure relief valve regulates the system pressure using an integrated pressure limiter.
  • the pressure build-up for the traction control is carried out via a self-priming return pump, the pump drawing brake fluid from the master brake cylinder.
  • the pressure relief valve allows excess brake fluid to flow back to the main cylinder. Since the pump is designed as a single-piston pump, strong periodic pressure fluctuations can occur behind the pump.
  • the pressure relief valve mentioned responds to the periodic pressure fluctuations in such a way that it opens to the brake line when the opening pressure is reached and allows liquid to flow suddenly to the master cylinder. Such an outflow process takes about a third of the pump period.
  • Hydraulic brake system characterized gekenn ⁇ characterized in that the support wall (57) is covered with a cover (60) to the outside.
  • Hydraulic brake system according to one of claims 1 to 10, characterized in that a housing of the memory (33, 33.1) is screwed to a housing block (31) of the traction control device and / or an anti-lock device.
  • Hydraulic brake system characterized gekenn ⁇ characterized in that a connector (41) with two L-shaped channels (42 and 43) for the fluid passage and with a screw connection (52) is provided.
  • Hydraulic brake system according to one of claims 1 to 10, characterized in that the memory (33.1) in a housing block (31) of a traction control device and / or an anti-lock device is integrated.
  • Hydraulic Bre sstrom according to one of claims 12 to 14, characterized in that the memory (33) in the main brake-side brake line (20) is inserted.
  • Hydraulic brake system according to claim 12 or 14, characterized in that the memory (33.1) between an input of the high pressure pump (29) and a shut-off valve (28) which is open during traction control operation is connected.
  • installation at this second point is also advantageous because there is a positive influence, i.e. Reduction of pressure peaks, when cooling occurs, the brake fluid contracts and wants to generate negative pressure in the shut-off line branch between the shut-off valve and the pump inlet, which is avoided by the flexible separating element in the accumulator.
  • Both possible installation locations for the accumulator according to the invention have in common the property that an equalization of the suction flow into the pump is achieved and that disadvantageous pressure peaks are avoided during traction control operation.
  • the special clamping of the membrane separating element is an advantage. It is also advantageous that the chamber located behind the separating element has the possibility of air refilling by using a porous or small perforated partition in order to allow the membrane to vibrate only as a rubber spring or to possibly move out of the chamber through the partition into the system Liquid contained in the diffused gas to be replaced by ambient air.
  • FIG. 1 shows a hydraulic circuit diagram of a 2-circuit brake system with anti-lock protection and traction control system and with one brake line connected to a brake line Memory
  • Figures 2 and 3 each have a longitudinal section through two such constructed storage
  • Figure 4 shows another design of such a memory.
  • FIG. 1 shows a hydraulic brake system 10 with a master brake cylinder 11 which carries a pressure medium reservoir 12.
  • Two brake circuits I and II are connected to the master brake cylinder 11.
  • the brake circuit I is used to actuate a wheel brake 13 assigned to the left front wheel and a wheel brake 14 of the vehicle assigned to the right rear wheel.
  • a wheel brake 15 of the right front wheel and a wheel brake 16 of the left rear wheel of the vehicle are connected to the brake circuit II.
  • This hydraulic brake system 10 therefore has a so-called diagonal division of the brake circuits.
  • the brake system 10 is equipped with a traction control device 17 for limiting traction slip on the driven front wheels of the vehicle.
  • the structure of the brake system 10 is described below with reference to the brake circuit II, which is equipped in the same way as the brake circuit I, insofar as this requires an understanding of the traction control device 17.
  • the brake system 10 has an outgoing from the master cylinder 11 and leading to the wheel brake 15 Bre line 20.
  • the brake line 20 is assigned a pressure control valve arrangement 21 for the brake pressure modulation of the wheel brake 15.
  • Such a pressure control valve arrangement 21 consists of an inlet valve 22 and an outlet valve 23, which are designed as 2/2-way valves.
  • a pressure limiting valve 24 is arranged in the brake line 20 on the master cylinder side.
  • the pressure relief valve 24 has a basic position 24a in which it is permeable to pressure medium. In a working position 24b, the pressure relief valve 24 blocks the brake line 20; when a predetermined response pressure is exceeded, it is permeable in the direction of the master brake cylinder 11.
  • a suction line 27 branches off from the brake line 20 between the master brake cylinder 11 and the pressure limiting valve 24, in which an ASR shut-off valve 28 designed as a 2/2-way valve lies. In its basic position 28a, this blocks the suction line 27; in its working position 28b, the suction line is free.
  • the suction line 27 leads to the suction line of a self-priming high-pressure pump 29, from the pressure side of which a pressure line 30 extends, which is connected to the brake line 20 between the pressure limiting valve 24 and the pressure control valve arrangement 21.
  • the elements of the brake system 10 located between the master brake cylinder 11 and the wheel brakes 13 to 16 are combined in a housing block 31, the housing 32 of which is indicated by a dash-dotted line.
  • the brake circuit II is provided with an unpressurized, passive memory 33. This is either arranged in the brake line 20 or it is located on the suction line 27 downstream of the ASR shut-off valve 28; there it bears the reference number 33.1 and is only shown in broken lines.
  • An electronic control unit 37 which monitors the wheel turning behavior of the vehicle wheels with the aid of speed sensors 38 assigned to the vehicle wheels and, if disadvantageous drive slip occurs, the valves 22, 23, 24, 28 mentioned and an electric drive motor 39 of the high-pressure pump 29 switches according to a predetermined control algorithm. If disadvantageously large drive slip occurs, for example on the right front wheel of the vehicle assigned to the wheel brake 15, the control unit 37 switches the pressure relief valve 24 into the working position 24b, the ASR shut-off valve 28 into the working position 28b and the drive motor 39 of the high-pressure pump 29. The high-pressure pump 29 now sucks pressure medium from the reservoir 33 through the section 20.1 of the brake line 20 on the master cylinder side and through the suction line 27.
  • the pressure medium conveyed is conveyed through the pressure line 30 into the section 20.2 of the brake line 20 on the wheel side and passed into the wheel brake 15 for generating brake pressure so that a reduction in the drive slip is achieved via the braking action.
  • Phases for brake pressure maintenance and brake pressure reduction which are not described in more detail, can follow a brake pressure build-up of this type.
  • the memory 33 which is shown only as a symbol in FIG. 1, has the following construction, shown in FIG. 2:
  • a connecting piece 41 made from a hexagon piece two L-shaped channels 42, 43 are provided, one (42) of which represents, for example, an inlet and the other (43) an outlet.
  • the channel 42 communicates with a storage chamber 44.
  • the other channel 43 also communicates with the storage chamber 44, for example by way of a detour through an annular chamber 45 created by turning, which is also connected to the storage chamber 44 and which is otherwise connected by a transverse bore 46 the storage chamber 44 receiving block 47 is covered.
  • Sealing rings 50 and 51 are inserted into two recesses 48 and 49, and the connecting piece 41 is screwed to a nut 53 or the housing block 31 via a screw connection 52 in such a way that the seals 50 and 51 seal the feed chamber 44 from the outside.
  • the storage chamber 44 is covered by a membrane 54 and over the Membrane 54 is an air or gas chamber 55.
  • the membrane 54 forms a separating element between the air or gas chamber 55 and the hydraulic system, which is connected to the storage chamber 44.
  • Membranes made of elastomers, which have sufficient flexibility, are advantageous.
  • EPDM mixtures with high elasticity and Shore hardnesses of 70 to 80 Shore A are usually selected in brake systems.
  • the membrane 54 has at its clamping point an annular bead 56 which is pressed by a support wall 57 against a housing shoulder 58, in a manner similar to that which is common with brake light switches.
  • the membrane environment i.e. the housing and the support wall 57, are designed such that the membrane 54 can deform in both directions on its axis of symmetry. This is the only way to smooth dynamic vacuum areas and pressure peaks in the system.
  • the support wall 57 is held in the housing by means of a flange 59.
  • a cover 60 provides cover to the outside. The air or
  • Gas chamber 55 has, when an installation according to FIG.
  • ... 3 3 is selected, a volume of approximately 50 mm to max. 150 mm to the
  • the accumulator 33 has a particularly good damping effect if the gas spring effect of the gas trapped in the air or gas chamber 55 is used .
  • a very slow permeation of the gas through the membrane 54 into the liquid and the associated gas loss can be counteracted if a gas replenishment via a completely or partially gas-permeable support wall 57 he follows.
  • the support wall 57 is either made of a porous material, for example sintered material, or it is provided with a small-caliber through hole 61. Variants from very tight to completely leaky are possible.
  • Sintered support walls 57 for example made of stainless steel alloy powder with a density of 6.6 to, are particularly suitable
  • Such support walls 57 have on the one hand a sufficient gas permeability of 0.5 to 1.6 ml / s, but on the other hand they provide a sufficiently large one in dynamic operation
  • Another advantage of a sintered support wall 57 is that the production of the support wall with its special contour is inexpensive.
  • a simple design is also a solution in which, instead of an air or gas spring, only the deformation and restoring force of the membrane, i.e. the elastomer, is used.
  • a membrane arrangement is shown in FIGS. 3 and 4. It can be seen that here a membrane 62 has a hump 63 with which it can additionally be supported on the support wall 57. In this way, the air or gas chamber 55 is then divided into two concentric annular chambers 55.1 and 55.2 when the membrane 62 is supported. An initial structure of the membrane 62 is shown in dashed lines. A membrane 62 designed in this way can counteract a pressure of up to approximately 10 bar and also deform back again at a lower liquid pressure.
  • the membrane 62 is supported with the hump 63 on the leaking support wall 57, for example, and cannot be damaged thereby.
  • the leaky support wall 57 thus acts as a burst protection.
  • the support wall 57 does not have to be gas-permeable, for example, it can also be tight.
  • the hump 63 avoids that when air or gas permeates through the membrane 62, the entire surface of the membrane 62 lies against the support wall 57 during the period of time required for the filled-in liquid to vent with air through the master brake cylinder 11 to saturate the environment.
  • the double “L” channel guide in the housing 41 according to FIG. 2 was chosen because in the storage chamber 44, if the storage 33 is installed behind the ASR shut-off valve 28, a fine-pearled gas excretion can occur, which occurs in so-called dead water Foam and gas bubbles accumulated. These make the hydraulic brake system soft. Gas bubbles can also be entrained in the flow and get into the pump 29, where they impair the delivery rate.
  • the double "L" channel guide there is a cross hole with a guide piece.
  • Braking does not matter. It is also possible to integrate the memory 33.1 directly into the housing block 31. It can be caulked in or screwed in, or it can be molded in directly. In the latter case, the housing block 31 receives the necessary contour by means of a processing tool, then the membrane 54 or 62 is inserted and the support wall 57 is placed thereon, which in turn, with the appropriate housing block material, either caulked directly into the housing or, as in the figure 4 is shown, is fixed by means of a threaded screw 64. Furthermore, an inflow and an outflow line 65 and 66 can be seen, the arrangement of which ensures a good flushing of a storage chamber 67. Also advantageous are vertically offset or parallel offset lines up to tangential and axial inflows and outflows or vice versa.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Electromagnetism (AREA)
  • Regulating Braking Force (AREA)

Abstract

L'invention concerne un système de freinage hydraulique (10) comportant un système de régulation antipatinage (17), qui est pourvu d'un réservoir (33, 33.1) servant d'une part à compléter de manière appropriée le volume de liquide manquant pour rendre homogène le débit entrant d'une pompe haute pression (29) et d'autre part à éviter la formation de pics de pression dans le système. Le réservoir (33, 33.1) comporte une paroi mobile se présentant sous forme de membrane (54) qui peut se déplacer des deux côtés depuis une position centrale. Ce système de freinage hydraulique (10) s'utilise dans des automobiles.
PCT/DE1994/001197 1993-10-26 1994-10-12 Systeme de freinage hydraulique WO1995011824A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4336464.0 1993-10-26
DE19934336464 DE4336464B4 (de) 1993-10-26 1993-10-26 Hydraulische Bremsanlage

Publications (1)

Publication Number Publication Date
WO1995011824A1 true WO1995011824A1 (fr) 1995-05-04

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ID=6501028

Family Applications (1)

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PCT/DE1994/001197 WO1995011824A1 (fr) 1993-10-26 1994-10-12 Systeme de freinage hydraulique

Country Status (2)

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DE (1) DE4336464B4 (fr)
WO (1) WO1995011824A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19538615A1 (de) * 1995-10-17 1997-04-24 Teves Gmbh Alfred Hydraulische Bremsanlage mit Pulsationsdämpfer
US5735314A (en) * 1995-05-31 1998-04-07 Robert Bosch Gmbh Hydraulic accumulator for a brake system
US6142583A (en) * 1996-04-06 2000-11-07 Continental Teves Ag & Co. Ohg Anti-locking hydraulic motor vehicle brake system
US6702402B1 (en) 1999-03-25 2004-03-09 Aisin Seiki Kabushiki Kaisha Vehicular braking force control apparatus
EP2103494A1 (fr) * 2008-03-20 2009-09-23 Peugeot Citroën Automobiles S.A. Système de contrôle de stabilité et de trajectoire d'un véhicule automobile utilisant un servofrein actif
EP2103493A1 (fr) * 2008-03-20 2009-09-23 Peugeot Citroën Automobiles S.A. Système de contrôle de stabilité et de trajectoire d'un véhicule automobile utilisant un servofrein actif
EP2127977A1 (fr) * 2008-05-28 2009-12-02 Peugeot Citroën Automobiles S.A. Système de contrôle de stabilité et de trajectoire d'un véhicule automobile utilisant un servofrein actif
US9234531B2 (en) 2012-06-29 2016-01-12 Kelsey-Hayes Company Damping element for a motor vehicle hydraulic system
CN112368192A (zh) * 2018-07-07 2021-02-12 罗伯特·博世有限公司 具有分隔元件的压力设备
DE102022000439A1 (de) 2022-02-04 2022-04-07 Mercedes-Benz Group AG Befestigungselement für eine Bremsleitung
DE102022002619A1 (de) 2022-07-18 2022-09-01 Mercedes-Benz Group AG Verbindungselement für Bremsleitungen

Families Citing this family (25)

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Publication number Priority date Publication date Assignee Title
DE4402734C2 (de) * 1994-01-29 2003-06-05 Continental Teves Ag & Co Ohg Bremsschlupf- und antriebsschlupfgeregelte Bremsanlage
DE19524920A1 (de) * 1995-07-08 1997-01-09 Bosch Gmbh Robert Schwingungsdämpfer zur Dämpfung von Flüssigkeitsschwingungen in einem hydraulischen, schlupfgeregelten Bremssystem von Kraftfahrzeugen
DE19524921B4 (de) * 1995-07-08 2006-08-31 Robert Bosch Gmbh Schwingungsdämpfer zur Dämpfung von Flüssigkeitsschwingungen in einem hydraulischen, schlupfgeregelten Bremssystem von Kraftfahrzeugen
DE19534219A1 (de) * 1995-09-15 1997-03-20 Teves Gmbh Alfred Hydraulisch betätigtes Umschaltventil
DE19539780A1 (de) * 1995-10-26 1997-04-30 Bosch Gmbh Robert Schwingungsdämpfer zur Dämpfung von Flüssigkeitsschwingungen in einem hydraulischen, schlupfgeregelten Bremssystem von Kraftfahrzeugen
DE19544223B4 (de) * 1995-11-28 2005-11-24 Robert Bosch Gmbh Schwingungsdämpfer zur Dämpfung von Flüssigkeitsschwingungen in einem hydraulischen, schlupfgeregelten Bremssystem von Kraftfahrzeugen
DE19544221A1 (de) * 1995-11-28 1997-06-05 Bosch Gmbh Robert Dämpfer, insbesondere zur Dämpfung von Druckschwankungen in Bremsflüssigkeit hydraulischer Fahrzeugbremsanlagen
DE19626305A1 (de) * 1996-07-01 1998-01-08 Teves Gmbh Alfred Hydraulische Bremsanlage mit einer Einrichtung zur Aktivbremsung
DE19642792A1 (de) * 1996-10-17 1998-04-23 Bosch Gmbh Robert Schwingungsdämpfer, insbesondere für eine hydraulische, schlupfgeregelte Fahrzeugbremsanlage
DE19722550A1 (de) * 1997-05-28 1998-12-03 Itt Mfg Enterprises Inc Druckminderungs- und Dämpfungseinrichtung für Kraftfahrzeugbremsanlagen
DE19753308A1 (de) * 1997-12-02 1999-06-10 Itt Mfg Enterprises Inc Membranspeicher
DE19806724B4 (de) * 1998-02-18 2005-02-17 Continental Teves Ag & Co. Ohg Bremsanlage mit Pulsationsdämpfer
DE19814835A1 (de) * 1998-04-02 1999-10-07 Itt Mfg Enterprises Inc Elektronisch geregelte Bremsanlage mit Speicher
DE19841152A1 (de) * 1998-04-07 1999-10-14 Continental Teves Ag & Co Ohg Blockiergeschützte Kraftfahrzeug-Bremsanlage
DE19850910A1 (de) 1998-11-05 2000-05-11 Bosch Gmbh Robert Druckmittelspeicher für Fahrzeug-Bremsanlagen
DE19948444B4 (de) * 1998-11-13 2007-05-16 Continental Teves Ag & Co Ohg Dämpfer
WO2001081812A1 (fr) 2000-04-20 2001-11-01 Continental Teves Ag & Co. Ohg Amortisseur d'oscillations
DE10318613B3 (de) * 2003-04-25 2005-01-20 Robert Bosch Gmbh Vorrichtung zur Dämpfung von Druckpulsationen, insbesondere in einem Druckmittelkreis sowie deren Verwendung
US7338136B2 (en) * 2004-12-16 2008-03-04 Honda Motor Co., Ltd. Electronic braking device
DE102004061811B4 (de) * 2004-12-22 2017-12-21 Robert Bosch Gmbh Drucksystem mit wenigstens zwei Druckkreisen
DE102005009658B4 (de) * 2005-02-02 2014-05-22 Continental Teves Ag & Co. Ohg Hydraulikaggregat
DE102011089183A1 (de) * 2011-12-20 2013-06-20 Robert Bosch Gmbh Druckpulsationsdämpfer für eine Fahrzeugbremsanlage
DE102013221690A1 (de) 2013-10-25 2015-04-30 Robert Bosch Gmbh Bremsanlage
JP6725985B2 (ja) * 2015-12-24 2020-07-22 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツングＲｏｂｅｒｔ Ｂｏｓｃｈ Ｇｍｂｈ 車両用のブレーキシステムの液圧制御ユニット
DE102019200204A1 (de) 2019-01-10 2020-07-16 Robert Bosch Gmbh Bremssystemdämpfer mit einer Dämpferkammer

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EP0456597A1 (fr) * 1990-05-07 1991-11-13 Richard A. Cardenas Dispositif de contrôle de pression réglable pour systèmes de freinage hydraulique
DE4128386A1 (de) * 1991-08-27 1993-03-04 Bosch Gmbh Robert Hydraulische bremsanlage mit einer antriebsschlupfregeleinrichtung, insbesondere fuer kraftfahrzeuge
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FR2067857A5 (fr) * 1969-11-19 1971-08-20 Farman Charles
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WO1990012713A1 (fr) * 1989-04-22 1990-11-01 Alfred Teves Gmbh Dispositif de freinage a regulation du glissement, notamment pour vehicules a moteur
EP0456597A1 (fr) * 1990-05-07 1991-11-13 Richard A. Cardenas Dispositif de contrôle de pression réglable pour systèmes de freinage hydraulique
DE4128386A1 (de) * 1991-08-27 1993-03-04 Bosch Gmbh Robert Hydraulische bremsanlage mit einer antriebsschlupfregeleinrichtung, insbesondere fuer kraftfahrzeuge
EP0539898A1 (fr) * 1991-10-30 1993-05-05 Sumitomo Electric Industries, Limited Dispositif de contrôle de pression de fluide de freinage
EP0539899A1 (fr) * 1991-10-30 1993-05-05 Sumitomo Electric Industries, Limited Dispositif de contrôle de pression de fluide de freinage

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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5735314A (en) * 1995-05-31 1998-04-07 Robert Bosch Gmbh Hydraulic accumulator for a brake system
DE19538615A1 (de) * 1995-10-17 1997-04-24 Teves Gmbh Alfred Hydraulische Bremsanlage mit Pulsationsdämpfer
WO1997014591A1 (fr) * 1995-10-17 1997-04-24 Itt Automotive Europe Gmbh Systeme de freinage hydraulique avec amortisseur de pulsations
DE19538615B4 (de) * 1995-10-17 2007-11-15 Continental Teves Ag & Co. Ohg Hydraulische Bremsanlage mit Pulsationsdämpfer
US6142583A (en) * 1996-04-06 2000-11-07 Continental Teves Ag & Co. Ohg Anti-locking hydraulic motor vehicle brake system
US6702402B1 (en) 1999-03-25 2004-03-09 Aisin Seiki Kabushiki Kaisha Vehicular braking force control apparatus
FR2928890A1 (fr) * 2008-03-20 2009-09-25 Peugeot Citroen Automobiles Sa Systeme de controle de stabilite et de trajectoire d'un vehicule automobile utilisant un servofrein actif
EP2103493A1 (fr) * 2008-03-20 2009-09-23 Peugeot Citroën Automobiles S.A. Système de contrôle de stabilité et de trajectoire d'un véhicule automobile utilisant un servofrein actif
EP2103494A1 (fr) * 2008-03-20 2009-09-23 Peugeot Citroën Automobiles S.A. Système de contrôle de stabilité et de trajectoire d'un véhicule automobile utilisant un servofrein actif
FR2928889A1 (fr) * 2008-03-20 2009-09-25 Peugeot Citroen Automobiles Sa Systeme de controle de stabilite et de trajectoire d'un vehicule automobile utilisant un servofrein actif
EP2127977A1 (fr) * 2008-05-28 2009-12-02 Peugeot Citroën Automobiles S.A. Système de contrôle de stabilité et de trajectoire d'un véhicule automobile utilisant un servofrein actif
FR2931763A1 (fr) * 2008-05-28 2009-12-04 Peugeot Citroen Automobiles Sa Systeme de controle de stabilite et de trajectoire d'un vehicule automobile utilisant un servofrein actif
US9234531B2 (en) 2012-06-29 2016-01-12 Kelsey-Hayes Company Damping element for a motor vehicle hydraulic system
CN112368192A (zh) * 2018-07-07 2021-02-12 罗伯特·博世有限公司 具有分隔元件的压力设备
CN112368192B (zh) * 2018-07-07 2023-04-21 罗伯特·博世有限公司 具有分隔元件的压力设备
DE102022000439A1 (de) 2022-02-04 2022-04-07 Mercedes-Benz Group AG Befestigungselement für eine Bremsleitung
DE102022002619A1 (de) 2022-07-18 2022-09-01 Mercedes-Benz Group AG Verbindungselement für Bremsleitungen

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DE4336464A1 (de) 1995-04-27
DE4336464B4 (de) 2005-11-17

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