WO2009065710A1 - Dispositif de freinage électro-hydraulique - Google Patents

Dispositif de freinage électro-hydraulique Download PDF

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Publication number
WO2009065710A1
WO2009065710A1 PCT/EP2008/064664 EP2008064664W WO2009065710A1 WO 2009065710 A1 WO2009065710 A1 WO 2009065710A1 EP 2008064664 W EP2008064664 W EP 2008064664W WO 2009065710 A1 WO2009065710 A1 WO 2009065710A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
brake
brake system
hydraulic
control valve
Prior art date
Application number
PCT/EP2008/064664
Other languages
German (de)
English (en)
Inventor
Lothar Schiel
Peter Rieth
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
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2009065710A1 publication Critical patent/WO2009065710A1/fr

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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
    • B60T8/40—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 comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4072—Systems in which a driver input signal is used as a control signal for the additional fluid circuit which is normally used for braking
    • B60T8/4077—Systems in which the booster is used as an auxiliary pressure source

Definitions

  • the present invention relates to an electrohydraulic brake system for motor vehicles of the "brake-by-wire" type having a master brake cylinder which can be actuated by means of a brake pedal and has a pressure medium reservoir associated with the master brake cylinder, a travel simulator cooperating with the master brake cylinder.
  • Brake-by-wire "gives the driver a preselected compliance on the brake pedal, a controllable by an electronic control unit pressure source, which is formed of a motor-driven hydraulic pump and a high-pressure accumulator can be charged by the pump and the pressure wheel brakes of the motor vehicle are acted upon , with brake pressure piston, which limit in a housing brake pressure chambers, with which the wheel brakes with the interposition of a Radtikmodulations worn with two return pumps are connected, as well as with a Druckregelv This is actuated by a pressure applied in the master cylinder is and which serves to control the pressure provided by the pressure source.
  • Such a brake system is known from DE 10 2006 019 040 Al.
  • the special feature of the known brake system are cylinder-piston arrangements, which are provided in the chain of effects between the pressure source and the wheel brakes, the pressure control valve and cylinder-piston assemblies actuated by the pressure provided by the pressure control valve or the pressure provided by the master cylinder pressure are.
  • Particularly disadvantageous is the complex construction of the cylinder-piston arrangements, which have both the above-mentioned brake pressure pistons and reaction pistons in which components of the travel simulator are integrated.
  • the brake pressure piston are arranged in at least one bore of an electro-hydraulic unit and can be actuated by a pressure booster piston, which is acted upon by the regulated pressure by the pressure regulating valve.
  • the brake pressure piston in a bore of the electro-hydraulic unit are arranged one behind the other.
  • the brake pressure piston can be arranged side by side in two holes of the electro-hydraulic unit.
  • the brake pressure chambers are connected to master cylinder pressure chambers, wherein the connections can be shut off by means of isolation valves. This measure is particularly useful when using the brake system according to the invention in the "brake-by-wire" mode.
  • the pressure control valve is additionally actuated by a pressure controlled in a pilot chamber pressure, which is derived from the provided by the pressure source hydraulic pressure.
  • Another advantageous embodiment of the invention is that between the master cylinder and the travel simulator, a 2/2-way switching valve is connected, which is switchable by the pressure provided by the pressure source.
  • An increase in the reliability of the brake system according to the invention is achieved in another embodiment in that a connected to the suction side of the pump second pressure fluid reservoir, the pump with the high-pressure accumulator, a suction side of the pump to the pilot chamber of the pressure control valve line connecting a A line for driving a 2/2-way switching valve for separating the travel simulator from the master cylinder, a line between the pressure source and the pilot chamber of the pressure control valve, an input of the pressure control valve to the pressure source line connecting the pressure control valve and a line between the output of the pressure control valve and a Form face of the pressure booster piston form a dynamic pressure medium circuit, which is separated by the pressure booster piston of hydrostatic pressure medium circuits passing through the pressure chambers of the master cylinder, a connecting line between a pressure chamber and the travel simulator, a connecting line between the pressure chamber and the pressure control valve, connecting lines between the pressure chambers and the brake pressure chambers , Connecting lines between the brake pressure chambers and the Radtigmodulations recognized and the connections between the wheel pressure modulation device and the
  • a precise control of einwinbaren in the pilot chamber pressure is achieved in a further embodiment of the subject invention in that in the line section between the high pressure accumulator and the pilot chamber of the pressure control valve, an electromagnetically actuated, analog controllable 2/2-way valve, preferably a normally closed (SG) Valve, is inserted.
  • an electromagnetically operable, analog controllable 2/2-way valve preferably a normally open (SO) valve inserted is in the line section between the second pressure fluid reservoir or the suction side of the pump and the pilot chamber of the pressure control valve.
  • SO normally open
  • a redundant detection of the driver deceleration request is achieved in a further embodiment of the invention in that a displacement sensor for detecting the actuation path of the brake pedal or a braking request is provided and that a first pressure sensor is provided for detecting the pressure applied in the master cylinder pressure.
  • An advantageous development of the subject invention provides a second pressure sensor for detecting the pressure held by the high pressure accumulator before.
  • a third pressure sensor for detecting the pressure provided by the pressure regulating valve is provided.
  • Master cylinder provides that the first pressure medium reservoir and the second pressure fluid reservoir are designed as a single, three-chamber pressure fluid reservoir. By this measure it is achieved that all pressure medium chambers can be filled via a single filling opening.
  • the electrohydraulic brake system shown schematically in the drawing consists essentially of an actuatable by a brake pedal 1, two-circuit hydraulic pressure generator or master cylinder 2 in tandem design, cooperating with the tandem master cylinder 2 way simulator 3, a pressure medium reservoir 4, a schematically illustrated electro-hydraulic unit fifth , a hydraulic control unit HCU or a Radtikmodulations worn 6, to which the vehicle wheels associated wheel brakes 7, 8, 9, 10 are connected, and an electronic control unit 16.
  • a pressure source one with the reference numeral 13th provided pressure control valve assembly and two brake pressure piston 17, 18 are integrated, which limit in a bore 24 brake pressure chambers 27, 28, whose task will be explained below.
  • the actuating travel of the brake pedal 1 is detected by means of a displacement sensor 33, while a first pressure sensor 19 is used to determine the pressure applied in the master brake cylinder 2.
  • a first pressure sensor 19 is used to determine the pressure applied in the master brake cylinder 2.
  • unspecified wheel sensors are provided.
  • the known per se tandem master cylinder 2 has two pistons 11, 12, limited, separate pressure chambers 14, 15, on the one hand with the pressure medium reservoir. 4 and on the other hand by means of lines 26, 29 are connected to the brake pressure chambers 27, 28. In the lines 26, 29 separating valves 40, 41 are inserted, which are designed as electromagnetically operable, normally open (SO-) 2/2-way valves and serve to shut off the lines 26, 29.
  • SO- normally open
  • the above-mentioned pressure source is formed by a motor-pump unit 20, which consists of an electric motor 22 and a pump 23 driven by the electric motor 22, and a high-pressure accumulator 21 which can be charged by the pump 23.
  • the existing in the high-pressure accumulator 21 hydraulic pressure is monitored by a pressure sensor 55.
  • the above-mentioned pressure control valve assembly 13 which is formed in the example shown as a slide valve, is operatively connected between the pressure source 20, 21 and a brake pressure piston 17, 18 upstream pressure chamber 25 and on the one hand via a hydraulic piston 45 by the first pressure chamber 14 of the Master cylinder 2 actuated hydraulic pressure and on the other hand actuated by an electronically controlled hydraulic pressure, which is controlled in a pilot chamber 37.
  • the above-mentioned pressure chamber 25 is limited by a pressure booster piston 42, which is in force-transmitting connection with the first brake pressure piston 17.
  • the above-mentioned electronic pressure control by means of two electromagnetically actuated, analog controllable 2/2-way valves 35, 36 which are inserted in line sections 43, 44 which are connected to the pilot chamber 37 of the pressure control valve 13.
  • the pilot chamber 37 is limited on the one hand by the hydraulic piston 45 and on the other hand by a slide 30 which forms the valve body of the pressure control valve 13.
  • the the pilot control room 37 facing away from the surface of the piston 45 is acted upon by means of a connected to the line 26 line section 46 with the pressure in the first pressure chamber 14 of the master cylinder 2 pressure.
  • the line section 43 is connected to a hydraulic line 47, which connects the suction side of the pump 23 with a second pressure medium reservoir 48.
  • the second pressure medium reservoir 48 may preferably with the aforementioned first
  • Pressure medium reservoir 4 are combined to form a single, three-chamber pressure fluid reservoir.
  • Another line section 49 connects in the illustrated position of the slide 30, the line 47 with a limited by the slide 30 annular space which is connected to an output terminal 54 of the pressure control valve 13 to which the pressure chamber 25 is connected by means of a line section 57.
  • the line section 44 is connected to another hydraulic line 50, which communicates with the pressure side of the pump 23 and the output of the
  • High-pressure accumulator 21 is connected and which serves the hydraulic control of a 2/2-way valve 51, which serves to shut off a connected to the line 26 line section 52 and thus the separation of the travel simulator 3 from the master cylinder 2.
  • a 2/2-way valve 51 which serves to shut off a connected to the line 26 line section 52 and thus the separation of the travel simulator 3 from the master cylinder 2.
  • Another connected to the line 50 line section 53 allows applying the previously mentioned annulus or the output terminal 54 with the pressure provided by the high-pressure accumulator 21.
  • a further pressure sensor 56 is provided for monitoring the pressure provided by the pressure regulating valve 13.
  • the second pressure medium reservoir 48, the lines 47, 50, the line sections 43, 44, 53 and 57, the pressure control valve thirteenth and the pump 23 and the high pressure accumulator 21 form a hydrodynamic circuit.
  • hydraulic energy is kept ready in the high-pressure accumulator 21 in order to perform hydraulic staging work on the pressure booster piston 42 if necessary.
  • Losses of pressure medium - for example, by a small internal leakage at sealing gaps of the pressure control valve 13 - are easily compensated by means of the pressure control function, as well as any gas bubbles caused discontinuities in the pressure medium flow rates.
  • the driver deceleration request is detected redundantly by the displacement sensor 33 and the first pressure sensor 19, after which the isolation valves 40, 41 in their closed switching position are switched so that the brake pressure chambers 27, 28 are separated from the master cylinder 2.
  • a pressure fluid volume from the first pressure chamber 14 of the master cylinder 2 is displaced into the travel simulator 3.
  • Pressure booster piston 42 the brake pressure piston 17, 18 in the sense of an increase in pressure in the brake pressure chambers 27, 28 is actuated, so that an increase in pressure in the wheel brakes 7 - 10 takes place.
  • the brake system according to the invention is operated in a so-called "recuperation mode" in which the detected driver deceleration request is completely or partially provided by regenerative deceleration of the vehicle, the only task remaining is to accomplish the remaining deceleration difference with the friction brakes described "brake-by-wire" mode feasible without changing the brake pedal feel, even if the distribution ratio of the total deceleration in a Rekuperationsbremsanteil and a Reibbremsanteil changes dynamically during braking - for example, if the vehicle no Rekuperationsbremsenergy can be more recorded.
  • Pressure translator piston 42 is carried out by the pressure applied by the driver.
  • the pressure buildup in the brake pressure chambers 27, 28 prevents pressure fluid from flowing out of the master brake cylinder 2 into the brake pressure chambers 27, 28.
  • a recuperation brake is not provided function-ready brake electronics dispensable.

Landscapes

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

Abstract

La présente invention concerne un dispositif de freinage électro-hydraulique pour véhicule du type freinage câble (« brake-by-wire »). Le dispositif de freinage comporte, entre autres, un simulateur de course (3) coopérant avec un cylindre de frein maître (2), une source de pression (20) formée par une pompe hydraulique (23) et un réservoir haute pression (21), une soupape de réglage de pression (13) ainsi que deux pistons de pression de freinage (17, 18), lesquels délimitent des chambres de pression de freinage (27, 28) auxquelles sont raccordés des freins à roue (7-10) du véhicule. L'invention vise à obtenir un dispositif de freinage du type mentionné ci-dessus à un coût de fabrication raisonnable. A cette fin, les pistons de pression de freinage (17, 18) sont disposés dans au moins un alésage (24) d'une unité électro-hydraulique (5) et ils peuvent être actionnés par un piston multiplicateur de pression (42) qui peut être sollicité par la pression réglée par la soupape de réglage de pression (13).
PCT/EP2008/064664 2007-11-21 2008-10-29 Dispositif de freinage électro-hydraulique WO2009065710A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102007055510.7 2007-11-21
DE102007055510 2007-11-21
DE102008039305A DE102008039305A1 (de) 2007-11-21 2008-08-22 Elektrohydraulische Bremsanlage
DE102008039305.3 2008-08-22

Publications (1)

Publication Number Publication Date
WO2009065710A1 true WO2009065710A1 (fr) 2009-05-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/064664 WO2009065710A1 (fr) 2007-11-21 2008-10-29 Dispositif de freinage électro-hydraulique

Country Status (2)

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DE (1) DE102008039305A1 (fr)
WO (1) WO2009065710A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106427964A (zh) * 2016-02-05 2017-02-22 芜湖伯特利汽车安全系统股份有限公司 线控液压制动系统及其控制方法
US9937910B2 (en) 2015-11-12 2018-04-10 Robert Bosch Gmbh Braking system and method of operating the same
CN113147694A (zh) * 2014-05-20 2021-07-23 爱皮加特股份公司 用于车辆制动器的操纵系统和用于运行该操纵系统的方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0428320A1 (fr) * 1989-11-07 1991-05-22 Honda Giken Kogyo Kabushiki Kaisha Système de commande de la pression hydraulique
DE4003579C1 (en) * 1990-02-07 1991-06-27 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De Anti-lock brake circuit for motor vehicle - has variable volume pressure modulation chamber coupled to brakes by control valves
EP1180460A2 (fr) * 2000-08-16 2002-02-20 Toyota Jidosha Kabushiki Kaisha Système de freinage hydraulique comprenant un générateur de pression motorisé, et dispositif pour commander la pression de sortie du générateur de pression
DE102006019040A1 (de) * 2005-10-07 2007-04-26 Continental Teves Ag & Co. Ohg Elektrohydraulische Bremsanlage für Kraftfahrzeuge

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4415438A1 (de) * 1994-05-03 1995-11-09 Teves Gmbh Alfred Elektronisch regelbares Bremsbetätigungssystem
DE19725298B4 (de) * 1997-06-14 2006-02-09 Continental Teves Ag & Co. Ohg Elektronisch regelbares Bremsbetätigungssystem

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0428320A1 (fr) * 1989-11-07 1991-05-22 Honda Giken Kogyo Kabushiki Kaisha Système de commande de la pression hydraulique
DE4003579C1 (en) * 1990-02-07 1991-06-27 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De Anti-lock brake circuit for motor vehicle - has variable volume pressure modulation chamber coupled to brakes by control valves
EP1180460A2 (fr) * 2000-08-16 2002-02-20 Toyota Jidosha Kabushiki Kaisha Système de freinage hydraulique comprenant un générateur de pression motorisé, et dispositif pour commander la pression de sortie du générateur de pression
DE102006019040A1 (de) * 2005-10-07 2007-04-26 Continental Teves Ag & Co. Ohg Elektrohydraulische Bremsanlage für Kraftfahrzeuge

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113147694A (zh) * 2014-05-20 2021-07-23 爱皮加特股份公司 用于车辆制动器的操纵系统和用于运行该操纵系统的方法
CN113147694B (zh) * 2014-05-20 2024-02-13 爱皮加特股份公司 用于车辆制动器的操纵系统和用于运行该操纵系统的方法
US9937910B2 (en) 2015-11-12 2018-04-10 Robert Bosch Gmbh Braking system and method of operating the same
CN106427964A (zh) * 2016-02-05 2017-02-22 芜湖伯特利汽车安全系统股份有限公司 线控液压制动系统及其控制方法

Also Published As

Publication number Publication date
DE102008039305A1 (de) 2009-05-28

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