[go: up one dir, main page]

WO2010079011A1 - Ensemble pompe pour produire une pression de freinage dans un système de freinage - Google Patents

Ensemble pompe pour produire une pression de freinage dans un système de freinage Download PDF

Info

Publication number
WO2010079011A1
WO2010079011A1 PCT/EP2009/066022 EP2009066022W WO2010079011A1 WO 2010079011 A1 WO2010079011 A1 WO 2010079011A1 EP 2009066022 W EP2009066022 W EP 2009066022W WO 2010079011 A1 WO2010079011 A1 WO 2010079011A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
pump unit
brake circuit
eccentric cam
circuit
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
PCT/EP2009/066022
Other languages
German (de)
English (en)
Inventor
Reiner Fellmeth
Erwin Sinnl
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 WO2010079011A1 publication Critical patent/WO2010079011A1/fr
Anticipated expiration legal-status Critical
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
    • B60T8/40—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
    • B60T8/4031—Pump units characterised by their construction or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0536—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units
    • F04B1/0538—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units located side-by-side

Definitions

  • the invention relates to a pump unit for generating brake pressure in a brake system according to the preamble of claim 1.
  • a hydraulic vehicle brake system which is designed as a dual-circuit brake system with two connected to a common master cylinder brake circuits, each brake circuit acts on two wheel brake on the wheels.
  • the vehicle brake system is equipped with a hydraulic pump unit, consisting of a respective one brake circuit associated hydraulic pump and a common, both hydraulic pumps actuated electric motor.
  • a hydraulic pump unit consisting of a respective one brake circuit associated hydraulic pump and a common, both hydraulic pumps actuated electric motor.
  • the invention is based on the object, with simple constructive measures, to adapt a pump unit for generating brake pressure in a brake system with at least two hydraulic brake circuits to the pump delivery flows required per brake circuit.
  • the pump unit according to the invention is used in brake systems of vehicles, which are provided with at least two hydraulic brake circuits, each of which is assigned at least one wheel brake device.
  • the pump unit generates the required hydraulic pressure per brake circuit.
  • the pump unit has at least one delivery piston per brake circuit, wherein each delivery piston is to be driven via an eccentric cam assigned to it and the eccentric cams are arranged on a common shaft. When the shaft rotates, the delivery pistons resting against the contour of the eccentric cam are driven. Since only one shaft is provided for all eccentric cams, a single drive unit which drives the shaft, for example an electric motor, is sufficient for both brake circuits.
  • the eccentric cams have different eccentricity for realizing different high delivery flows per brake circuit. Due to the different eccentricity, the delivery pistons are deflected to different degrees, and a correspondingly different hydraulic fluid delivery flow is established. Thus, the different high demands on the flow rates in the brake circuits are taken into account, especially in the case of a Bremsnikaufannon on a Vorderachsnik and a Schuachsnik, since in this case, the brake circuits have a very different elasticity due to different levels of braking requirements. For example, the Vorderachs Vietnamese has an elasticity in the order of 30 mm 3 / bar and the Schuachsnik an elasticity of about 15 mm 3 / bar.
  • the adaptation to the different brake circuit elasticities is achieved with simple design measures. To change the eccentricity or to adapt to the respective hydraulic flow rate per brake circuit is to be realized with relatively little design effort.
  • various measures for implementation into consideration On the one hand, it is possible to realize the different high flow rates alone over a non-circular outer contour of the eccentric cam, wherein the outer contours, relative to the axis of the shaft on which the eccentric cams are arranged, differ from each other.
  • the eccentric cams may also be arranged centrically to the shaft, so that the eccentricity is set solely by way of adaptation of the outer contour of the eccentric cams. Basically possible is a combination with an eccentric arrangement of the cams on the
  • disc-shaped, round eccentric cam can be provided which are arranged eccentrically on the shaft.
  • the different eccentricity is here set either via a different Exzenternell with which the cam axis relative to the shaft axis is radially displaced, and / or over a different outer radius of the eccentric cam. If necessary, it is sufficient to arrange eccentric cam with different outer diameter with the same eccentric on the shaft, since in this embodiment, the respective associated delivery pistons are subjected to different large radial deflection.
  • the two eccentric cams are seen in the axial direction of the shaft one behind the other, preferably immediately one behind the other or with only a small axial distance.
  • Recirculating eccentric cam preferably via an electric motor.
  • each brake circuit a plurality of delivery pistons which are each acted upon by an eccentric cam.
  • three delivery pistons are assigned to each brake circuit, which are arranged in particular at a 120 ° angle distance from one another and are grouped radially around the shaft with the eccentric cams.
  • each eccentric cam acts on all its associated delivery pistons.
  • Providing three delivery pistons per brake circuit has the advantage that lower pressure pulsations occur in the brake circuits.
  • the brake pressure can be controlled variable and better to the respective
  • the two brake circuits of the brake system are in particular in a front-axle brake circuit with two wheel brake devices on the two front wheels and a rear axle brake circuit with two wheel brake devices on the rear wheels.
  • a higher pump delivery flow of the hydraulic fluid is required in the front-axle brake circuit than in the rear-axle brake circuit, which is achieved via the different eccentricities of the eccentric cams.
  • FIG. 1 shows a hydraulic circuit diagram of a vehicle brake system with a front axle brake circuit and a rear axle brake circuit and with an ESP system, which has a pump unit with three delivery pistons per brake circuit,
  • FIG. 3 shows a section through the pump unit with a representation of two eccentric cams seated on a common shaft, which each drive the delivery pistons assigned to them, wherein the eccentric cams have a different eccentricity
  • the brake system 1 in a motor vehicle has two brake circuits 2 and 3, in which it is located in the
  • Embodiment is a front-axle brake circuit and a rear-axle brake circuit.
  • the two brake circuits 2, 3 are connected to a common master cylinder 4, which is assigned a brake fluid reservoir 5, wherein the master cylinder 4 is operated by the driver via the brake pedal 6.
  • the brake pedal 6 is associated with a pedal travel sensor 7 for measuring the pedal travel.
  • each brake circuit 2 3 is a changeover valve 12 which is connected to the master cylinder 4, wherein the changeover valves are opened in their de-energized normal position.
  • Each switching valve 12 is associated with a flow-through from the master cylinder to the respective wheel brake check valve, which is connected in parallel to the changeover valve.
  • inlet valves 13 which are also open in the de-energized state and which are associated with check valves, which are traversed by the wheel brakes in the direction of the master cylinder.
  • Each wheel brake device 8, 9, 10, 1 1 is associated with an exhaust valve 14, which is closed in the de-energized state.
  • the outlet valves 14 are connected to the suction side of a pump unit 15, which has in each case three individual pumps 16, 17, and 18 or 19, 20 and 21 per brake circuit 2, 3.
  • the pump unit 15 is also associated with an electric drive motor 22 which drives a shaft 23 which actuates the pumps 16 to 21.
  • the pressure side of the pumps 16 to 21 is connected to a line section between the switching valve 12 and the two inlet valves 13 per brake circuit.
  • the suction sides of the pumps 16 to 21 are also connected to a main switching valve 24, which are hydraulically connected to the master cylinder 4.
  • the main switching valves 24, which are closed in the de-energized state, can be opened so that the pumps 16 to 21 draw in hydraulic fluid directly from the master brake cylinder 4 for a rapid buildup of brake pressure.
  • the brake pressure build-up here is independent of an actuation of the brake system by the driver.
  • the pump unit 25 with the individual pumps 16 to 21, the electric drive motor 22 and the shaft 23 forms part of a driving dynamics assistance system, in particular an ESP system (electronic stability program).
  • a hydraulic accumulator 25 which serves for the interim storage of brake fluid, which omitted during a dynamic driving engagement through the exhaust valves 14 from the wheel brake 8 to 1 1 has been.
  • a check valve arranged in the connecting line between the outlet valves 14 and the suction side of the pumps 16 to 21, which can be flowed through in the direction of the suction side of the pumps.
  • Each brake circuit 2, 3 is associated with a respective pressure sensor 26 in the area of the wheel brake devices 8, 9 or 10, 11.
  • Another pressure sensor 27 is located in the brake circuit 2 adjacent to the master cylinder 4th
  • each brake circuit are assigned to three designed as a delivery piston individual pumps 16 to 18 and 19 to 21.
  • the delivery pistons of a brake circuit are each grouped around a disc-shaped eccentric cam 28 or 29 at an angle of 120 ° and are acted upon by the eccentric cam 28 and 29, respectively.
  • the eccentric cams 28 and 29 are arranged on the shaft 23 and rotate with the shaft 23, which is driven by the electric drive motor. Due to the eccentricity of the eccentric cam 28 and 29 results in the rotation of the shaft 23 at each delivery piston a radial actuation, so that each piston produces a delivery flow.
  • the height of the flow per brake circuit can be adjusted via the eccentricity of the respective eccentric cam 28 and 29, which are placed on the shaft 23 directly axially behind one another.
  • the eccentric cams 28 and 29 seated at a small axial distance from one another on the shaft 23 have a different degree with respect to the shaft 23 or the shaft axis 30 Eccentricity on.
  • the delivery pistons of each brake circuit are deflected to different degrees and accordingly also convey a different high hydraulic fluid volume flow.
  • Cam associated eccentric cam 28 a greater eccentricity than the second brake circuit associated eccentric cam 29th
  • the different sized eccentricities are, as shown in FIG. 4, referred to ei and e 2 .
  • the two eccentric cams 28 and 29 are each disk-shaped and have the same outer diameter.
  • the eccentricity is achieved by a radial offset ei or e 2 between the respective cam center axis 31 or 32 and the shaft axis 30 of the shaft 23. Since a higher volume flow is to be conveyed in the first brake circuit, the eccentric dimension ei of the first eccentric cam 28 is greater than the eccentric dimension e 2 of the second eccentric cam 29.
  • the eccentric cams 28 and 29 are arranged eccentrically offset by 180 ° relative to one another.
  • a typical eccentric dimension is for example for the front axle

Landscapes

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

Abstract

L'invention concerne un ensemble pompe (15) pour produire une pression de freinage dans un système de freinage, présentant deux circuits de freinage hydrauliques (82,3), auxquels est respectivement associé au moins un dispositif de freinage pour roue (8,9;10,11). L'ensemble pompe (15) présente au moins un piston d'alimentation (16,17,18; 19,20,21) par circuit de freinage (2,3), les pistons d'alimentation pouvant être entraînés par l'intermédiaire de cames excentriques (28,29), agencées sur un arbre commun (23). Les cames excentriques (28,29) présentent une excentricité différente (e1,e2).
PCT/EP2009/066022 2009-01-08 2009-11-30 Ensemble pompe pour produire une pression de freinage dans un système de freinage Ceased WO2010079011A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910000069 DE102009000069A1 (de) 2009-01-08 2009-01-08 Pumpeneinheit in einer Bremsanlage
DE102009000069.0 2009-01-08

Publications (1)

Publication Number Publication Date
WO2010079011A1 true WO2010079011A1 (fr) 2010-07-15

Family

ID=41604986

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/066022 Ceased WO2010079011A1 (fr) 2009-01-08 2009-11-30 Ensemble pompe pour produire une pression de freinage dans un système de freinage

Country Status (2)

Country Link
DE (1) DE102009000069A1 (fr)
WO (1) WO2010079011A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2749768A1 (fr) * 2012-12-28 2014-07-02 Mitsubishi Heavy Industries, Ltd. Machine hydraulique à pistons radiaux et générateur de turbine éolienne
WO2014202345A1 (fr) * 2013-06-18 2014-12-24 Danfoss Power Solutions Gmbh & Co Ohg Machine à fluide de travail
WO2018054937A1 (fr) * 2016-09-23 2018-03-29 Continental Teves Ag & Co. Ohg Procédé pour faire fonctionner un système de freinage

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023123961A1 (de) * 2023-09-06 2025-03-06 Pump Technology Solutions PS GmbH Radialkolbenpumpe, Verfahren zum Betrieb einer Radialkolbenpumpe und Lenksystem

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2697403A (en) * 1949-06-06 1954-12-21 Melba L Benedek Hydraulic pump or motor
JPS6025833A (ja) * 1983-07-20 1985-02-08 Akebono Brake Ind Co Ltd 車輪アンチロツク装置
DE4027794A1 (de) * 1990-09-01 1992-03-05 Teves Gmbh Alfred Hydraulische radialkolbenpumpe
DE19755678A1 (de) * 1996-12-16 1998-07-23 Unisia Jecs Corp Pumpenvorrichtung
WO1999064283A1 (fr) * 1998-06-05 1999-12-16 Robert Bosch Gmbh Systeme de freinage hydraulique pour vehicule
WO2005050015A1 (fr) * 2003-11-18 2005-06-02 Robert Bosch Gmbh Pompe a plusieurs pistons
WO2006066995A1 (fr) * 2004-12-22 2006-06-29 Robert Bosch Gmbh Dispositif d'entrainement
DE102007020503A1 (de) * 2007-05-02 2008-11-06 Robert Bosch Gmbh Hydraulische Fahrzeugbremsanlage und Verfahren zu deren Betrieb

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2697403A (en) * 1949-06-06 1954-12-21 Melba L Benedek Hydraulic pump or motor
JPS6025833A (ja) * 1983-07-20 1985-02-08 Akebono Brake Ind Co Ltd 車輪アンチロツク装置
DE4027794A1 (de) * 1990-09-01 1992-03-05 Teves Gmbh Alfred Hydraulische radialkolbenpumpe
DE19755678A1 (de) * 1996-12-16 1998-07-23 Unisia Jecs Corp Pumpenvorrichtung
WO1999064283A1 (fr) * 1998-06-05 1999-12-16 Robert Bosch Gmbh Systeme de freinage hydraulique pour vehicule
WO2005050015A1 (fr) * 2003-11-18 2005-06-02 Robert Bosch Gmbh Pompe a plusieurs pistons
WO2006066995A1 (fr) * 2004-12-22 2006-06-29 Robert Bosch Gmbh Dispositif d'entrainement
DE102007020503A1 (de) * 2007-05-02 2008-11-06 Robert Bosch Gmbh Hydraulische Fahrzeugbremsanlage und Verfahren zu deren Betrieb

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2749768A1 (fr) * 2012-12-28 2014-07-02 Mitsubishi Heavy Industries, Ltd. Machine hydraulique à pistons radiaux et générateur de turbine éolienne
WO2014202345A1 (fr) * 2013-06-18 2014-12-24 Danfoss Power Solutions Gmbh & Co Ohg Machine à fluide de travail
WO2014202344A1 (fr) * 2013-06-18 2014-12-24 Danfoss Power Solutions Gmbh & Co Ohg Machine à fluide de travail (machine à fluide de travail)
CN105209756A (zh) * 2013-06-18 2015-12-30 丹佛斯动力系统有限责任两合公司 流体工作机器
CN105209755A (zh) * 2013-06-18 2015-12-30 丹佛斯动力系统有限责任两合公司 流体工作机器
US20160356160A1 (en) 2013-06-18 2016-12-08 Artemis Intelligent Power Ltd. Fluid working machine
US10677058B2 (en) 2013-06-18 2020-06-09 Danfoss Power Solutions Gmbh & Co. Ohg Fluid working machine having offset valve cylinders
US10995739B2 (en) 2013-06-18 2021-05-04 Danfoss Power Solutions Gmbh & Co. Ohg Fluid working machine having first and second valve cylinder devices in fluid communication with each other via a common conduit
WO2018054937A1 (fr) * 2016-09-23 2018-03-29 Continental Teves Ag & Co. Ohg Procédé pour faire fonctionner un système de freinage
CN109789862A (zh) * 2016-09-23 2019-05-21 大陆-特韦斯贸易合伙股份公司及两合公司 用于运行制动系统的方法
US10953858B2 (en) 2016-09-23 2021-03-23 Continental Teves Ag & Co. Ohg Method for operating a brake system
CN109789862B (zh) * 2016-09-23 2021-07-02 大陆-特韦斯贸易合伙股份公司及两合公司 用于运行制动系统的方法

Also Published As

Publication number Publication date
DE102009000069A1 (de) 2010-07-15

Similar Documents

Publication Publication Date Title
EP2707262B1 (fr) Système de freinage hydraulique de véhicule comprenant un actionneur électromécanique et procédé permettant de faire fonctionner un tel système de freinage hydraulique de véhicule
EP2164730B1 (fr) Unité hydraulique pour réguler la pression de freinage d'une installation de frein d'un véhicule
EP2960124B1 (fr) Composant hydraulique pour une installation de freinage de vehicule automobile
DE102013206324A1 (de) Bremssystem für ein Fahrzeug und Verfahren zum Betreiben des Bremssystems
DE102010040854A1 (de) Hydraulisches Bremssystem sowie Verfahren zu dessen Betrieb
DE102010043403A1 (de) Hydraulische Fahrzeugbremsanlage
DE102008000873A1 (de) Verfahren zur Steuerung einer elektronisch schlupfregelbaren Fahrzeugbremsanlage
EP3665050B1 (fr) Système de freinage pour véhicules automobiles
EP3700786A1 (fr) Système de freinage et deux procédés pour faire fonctionner un tel système de freinage
WO2010079011A1 (fr) Ensemble pompe pour produire une pression de freinage dans un système de freinage
EP4003796B1 (fr) Procédé pour commander un système de frein hydraulique dans un véhicule
EP2268516B1 (fr) Générateur de pression d un dispositif de freinage hydraulique de véhicule et procédé de fonctionnement associé
DE102010062307A1 (de) Vorrichtung zum Aufnehmen und Abgeben von Hydraulikflüssigkeiten, insbesondere für ein Hybrid- oder Elektrofahrzeug, sowie Bremssystem für ein Hybrid- oder Elektrofahrzeug
DE102010003237A1 (de) Fahrzeugbremsanlage
DE10053993B4 (de) Hydraulische Bremsanlage und Verfahren zur Bremsdruckerzeugung und -regelung für Fahrzeugbremssystem
EP0862526A1 (fr) Systeme de freinage hydraulique avec source haute pression et soupape de dosage actionnee par la pedale
DE102004042028A1 (de) Fahrzeugbremsanlage mit einer Reib- und einer Rekuperationsbremse
EP1439992A1 (fr) Systeme de freinage electrohydraulique destine a des vehicules automobiles
EP3996960B1 (fr) Aggrégat hydraulique de pompe avec une valve de réduction de pression
WO1996013418A1 (fr) Systeme de freinage hydraulique pour controle de la tenue de route
DE102012211340A1 (de) Pumpengehäuse für ein Kraftfahrzeug-Hydroaggregat
EP3490856A1 (fr) Système de freinage hydraulique de véhicule
EP1881920B1 (fr) Systeme de regulation du freinage pour vehicules
DE102022002610B3 (de) Hydraulisches Bremssystem
EP4126612B1 (fr) Arrangement hydraulique dans un système de freins d'un véhicule et véhicule

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09760872

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 09760872

Country of ref document: EP

Kind code of ref document: A1