EP2238003A1 - Pompe à fluide hydraulique d'un système de freinage de véhicule, avec un entraînement excentrique - Google Patents

Pompe à fluide hydraulique d'un système de freinage de véhicule, avec un entraînement excentrique

Info

Publication number
EP2238003A1
EP2238003A1 EP08868502A EP08868502A EP2238003A1 EP 2238003 A1 EP2238003 A1 EP 2238003A1 EP 08868502 A EP08868502 A EP 08868502A EP 08868502 A EP08868502 A EP 08868502A EP 2238003 A1 EP2238003 A1 EP 2238003A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic fluid
fluid pump
hydraulic
designed
vehicle brake
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Withdrawn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
EP08868502A
Other languages
German (de)
English (en)
Inventor
Christian Doberschuetz
Werner Quirant
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 EP2238003A1 publication Critical patent/EP2238003A1/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Withdrawn legal-status Critical Current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
    • B60T8/40—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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element

Definitions

  • the invention relates to a hydraulic fluid pump of a vehicle brake system with a conveying means for conveying hydraulic fluid against an existing in a part of the vehicle brake hydraulic counter pressure. Furthermore, the invention relates to a vehicle brake system with such a hydraulic fluid pump.
  • Hydraulic fluid pumps of vehicle brake systems are known in which a plurality of reciprocating pumps are used as conveying means for conveying hydraulic fluid or brake fluid in the vehicle brake system, in particular for returning the brake fluid from the vehicle brakes and / or for active brake pressure buildup.
  • These reciprocating pumps are also referred to as pumple elements.
  • the pump elements are usually driven by an electric motor with a seated on a drive shaft eccentric.
  • cam drives or the like are possible. This results in dependence on the eccentricity of the eccentric and the diameter of the pump piston used in the pump element or the reciprocating pump, a constant delivery volume per revolution of the electric motor.
  • a hydraulic fluid pump of a vehicle brake system is provided with a conveying means for conveying hydraulic fluid against an existing in a part of the vehicle brake hydraulic counter pressure, wherein a means for varying the delivery volume of the conveying means is provided in dependence on the height of the hydraulic counter-pressure. Furthermore, the object is achieved according to the invention with affybrerasstrom with such configured according to the invention hydraulic fluid pump.
  • the largest possible hydraulic delivery capacity should be provided at a low pressure level or at a pressure level of 0 bar. With such a large hydraulic delivery capacity, the pressure build-up dynamics should be maximized or the time to overcome the ventilation clearance between the brake linings of the vehicle brake system and the associated brake disc should be minimized. This function of conventional vehicle brake systems also contributes to performance optimization
  • ABS antilock control
  • Fig. 1 shows as a graph on an X-axis plotted the pressure generated by pump elements in relation to a displayed on the associated Y-axis flow rate.
  • a pump element with high flow rate at low pressure level even at high pressure level still has a relatively high flow rate, as shown in Fig. 1 at the line 10.
  • the line 10 shows that between the hydraulic load torque (pressure) and the electrical power (capacity) of the associated drive motor is a linear relationship.
  • a pump element which is optimized at a first design point 20 at low pressure to a high delivery rate, promotes with increasing pressure according to the line 10 to a point 30, at which still a comparatively high delivery rate and thus , a relatively high control Amperage for the driving electric motor results.
  • a connection should be sought, as illustrated by the curve 70 in FIG.
  • the solution according to the invention achieves this optimized design curve by providing a means for varying the delivery volume of the delivery means as a function of the level of the hydraulic backpressure in the hydraulic delivery pump according to the invention.
  • a pump element or a reciprocating pump is provided as conveying means, wherein the delivery volume is defined as that amount of hydraulic fluid which pumps the hydraulic fluid pump into the associated vehicle brake system with a reciprocating motion of its reciprocating piston or with a reversal of its drive motor this sucks.
  • the solution according to the invention creates a need-based adaptation of the hydraulic delivery rate to the functional requirements of the associated control system. These requirements include, in particular, as explained, a high flow rate at low counter pressures for fast vehicle stabilization and low flow rate at high counter pressures for safe representation of the anti-lock functionality.
  • the conveying means for conveying Hydraulilcfmid is preferred according to the 'designed with at least one delivery piston slidably mounted in a cylinder, thereby defining a pressure chamber together with the cylinder whose volume is changed by the displacement of the conveyor piston.
  • the means for changing the delivery volume is preferably designed as a means for (additional) changing the volume of the pressure chamber as a function of the hydraulic counterpressure.
  • the resulting volume of the pressure chamber compared to the conventional situation is increased or kept larger when the delivery piston builds pressure while a high back pressure is applied.
  • the delivery piston then promotes less Hydraulikfiuid out of the pressure chamber. If, on the other hand, there is a slight counterpressure, when the hydraulic fluid is pushed out of the pressure chamber, its volume increases less or not at all, so that accordingly a greater amount of hydraulic fluid is exhausted from the pressure chamber.
  • the means for changing the volume of the pressure chamber as a function of the hydraulic back pressure is preferably designed as a means for changing the stroke of the delivery piston as a function of the hydraulic backpressure.
  • the resulting displacement of the delivery piston is advantageously reduced according to the invention with increasing back pressure, which increases the volume of the pressure chamber compared to the conventional situation and thus results in a lower hydraulic delivery.
  • an eccentric drive for displacing the delivery piston is also preferably provided and the means for
  • the adjusting device for changing the eccentricity of the eccentric drive is preferably designed by means of a bearing of the eccentric drive, in which the position of the bearing center point in the radial direction is variable. Such adjustment of the bearing center point can be made cost-effective and at the same time over the life of the associated hydraulic fluid pump away reliable.
  • the eccentric drive is further designed with three bearings arranged axially distributed, of which the position of the bearing center point in the radial direction can be changed in two bearings.
  • the two radially displaceable bearing lead to the above-explained, according to the invention intended adjustment of the stroke of the delivery piston, while the third, radially non-displaceable bearing provide the necessary guidance of the eccentric drive and in particular its electric motor.
  • the means for changing the delivery volume of the Förde ⁇ ffens is particularly preferably designed with an elastic element which can be tensioned against the back pressure of the hydraulic fluid.
  • an elastic element which can be tensioned against the back pressure of the hydraulic fluid.
  • the elastic element according to the invention advantageously designed with an annular elastomer component, which in particular surrounds the at least one bearing radially on the outside.
  • the use of at least two pump elements or reciprocating piston pumps is particularly preferably provided for each hydraulic brake circuit of the associated vehicle brake system.
  • at least one of the reciprocating pumps as conventionally operating pump designed with the then operatively required volume flow can be displayed even at high back pressures.
  • the requirements of the vehicle manufacturer can be met according to an overall significantly reduced current load of the associated vehicle electrical system, while at the same time the hydraulic 5 delivery rate can be displayed as needed.
  • Fig. 1 is a diagram of the ratio of flow rate and back pressure in conventional Hydraulikflmdpumpen and in a solution according to the invention
  • Fig. 2 is a greatly simplified longitudinal section of an exemplary embodiment of a hydraulic fluid pump according to the invention and 15
  • Figure 3 is a section m -. IE in Figure "2..
  • Fig. 1 As already explained above, it is shown how the solution according to the invention can be used to provide a delivery volume of a delivery device of a hydraulic fluid pump to a vehicle brake system that changes as a function of the magnitude of the hydraulic backpressure.
  • a delivery volume of a delivery device of a hydraulic fluid pump to a vehicle brake system that changes as a function of the magnitude of the hydraulic backpressure.
  • a hydraulic fluid pump 80 which as an essential component comprises an inlet valve 90, an inlet line 100, a cylinder 110 with a piston 120 arranged therein, an associated eccentric drive 130, an outlet line 140 and an outlet valve 150.
  • the eccentric drive 130 is formed with an electric motor 180 which drives a motor shaft 190.
  • the motor shaft 190 is rotatably mounted on two bearings 200 and 210, a floating bearing (bearing 200, this allows clearance compensation in the axial direction) and a fixed bearing (bearing 210, this leaves no Speilausrete in the axial direction).
  • a third, also designed as a floating bearing 220 is provided on the motor shaft 190.
  • an eccentric disc 230 is arranged rotationally fixed, whose axis is arranged offset radially to the axis of the motor shaft 190.
  • the bearing 200 (and also the optional bearing 220) is configured with a bearing inner race 240 (see FIG. 3) which is slid onto the motor shaft 190. Radially outside of the bearing inner race 240 (see FIG. 3) which is slid onto the motor shaft 190. Radially outside of the bearing inner race 240 (see FIG. 3)
  • Inner bearing ring 240 are distributed over the circumference of the bearing inner ring 240 a plurality of rolling elements 250 in the form of rolling elements, which are surrounded on the outside by a bearing outer ring 260.
  • This bearing outer ring 260 in turn is surrounded radially on the outside by an annular elastomer component 270, which in turn is surrounded by an outer ring 280.
  • the outer ring 280 serves to fix the bearing 200 in a housing (not further shown) of the hydraulic fluid pump 80.
  • the piston 120 is moved in the axial direction and offset relative to the cylinder 110.
  • the volume in the pressure chamber 160 is thereby alternately increased and decreased, whereby hydraulic fluid is sucked through the inlet conduit 110 into the pressure chamber 160 and subsequently challenged again by the outlet conduit 140 from the pressure chamber 160.
  • the piston 120 thus forms, together with the cylinder 110 and the eccentric drive 130, a conveying means for conveying hydraulic fluid against a hydraulic counter-pressure existing in a part of the vehicle brake system (present in the outlet line 140 and the outlet valve 150).
  • the piston 120 is clamped against the eccentric disc 230 which, as explained above, is mounted on the elastomer component 270 via the motor shaft 190 with the bearing 200 (and optionally the bearing 220).
  • This elastomeric component 270 forms a means for varying the delivery volume of this conveying means as a function of the level of the hydraulic counter-pressure.
  • the elastomeric component 270 mutes an offset of the bearing outer ring 260 relative to the outer ring 280 with a corresponding radial force.
  • This radial force acts on the bearing 200 (and also the bearing 220) via the eccentric disk 230 and the piston 120 as a function of the pending back pressure in the pressure chamber 160.
  • the piston 120 offset by the compliance of the elastomeric member 270 in the direction of increasing the volume in the pressure chamber 160 and thus it reduces the hydraulic delivery of the piston 120th
  • the bearing 210 may be provided with an elastomeric component 270 for this purpose. This leads directly to the fact that the required maximum starting torque of the eccentric drive 130 and the required electrical power can be reduced compared to conventional solutions.
  • the functionally required volume flow in the vehicle brake system or the brake fluid circuit associated with the hydraulic fluid pump 80 is ensured by a further (not shown) hydraulic fluid pump conventional type.
  • the associated vehicle brake system therefore preferably comprises at least two hydraulic fluid pumps per brake circuit, i. a total of at least four per each hydraulic unit.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Reciprocating Pumps (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Regulating Braking Force (AREA)

Abstract

L'invention concerne une pompe à fluide hydraulique (80) d'un système de freinage de véhicule, avec un moyen de transport (110, 120) pour transporter le fluide hydraulique à l'encontre d'une pression hydraulique antagoniste régnant dans une partie du système de freinage de véhicule (140, 150). Selon l'invention, il est prévu un moyen (270), de préférence un élément élastomère dans le palier d'arbre du moteur (200, 220), pour modifier le volume déplacé par le moyen de transport (110, 120) en fonction du montant de la pression hydraulique antagoniste.
EP08868502A 2007-12-21 2008-10-24 Pompe à fluide hydraulique d'un système de freinage de véhicule, avec un entraînement excentrique Withdrawn EP2238003A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007062031A DE102007062031A1 (de) 2007-12-21 2007-12-21 Hydraulikfluidpumpe einer Fahrzeugbremsanlage mit einem Exzenterantrieb
PCT/EP2008/064482 WO2009083290A1 (fr) 2007-12-21 2008-10-24 Pompe à fluide hydraulique d'un système de freinage de véhicule, avec un entraînement excentrique

Publications (1)

Publication Number Publication Date
EP2238003A1 true EP2238003A1 (fr) 2010-10-13

Family

ID=40297957

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08868502A Withdrawn EP2238003A1 (fr) 2007-12-21 2008-10-24 Pompe à fluide hydraulique d'un système de freinage de véhicule, avec un entraînement excentrique

Country Status (4)

Country Link
EP (1) EP2238003A1 (fr)
CN (1) CN101903225B (fr)
DE (1) DE102007062031A1 (fr)
WO (1) WO2009083290A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013114749A1 (de) * 2013-12-21 2015-06-25 Gerhard Stock Fördereinrichtung für ein Fluid
DE102016001576A1 (de) * 2016-02-11 2017-08-17 Wabco Gmbh Hubkolbenmaschine, insbesondere zwei- oder mehrstufiger Kolbenkompressor, Druckluftversorgungsanlage, Druckluftversorgungssystem und Fahrzeug, insbesondere PKW mit einer Druckluftversorgungsanlage

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4122486A1 (de) * 1991-07-06 1993-01-07 Teves Gmbh Alfred Antriebsaggregat, insbesondere motor-pumpenaggregat fuer schlupfgeregelte bremsanlagen
DE4241827A1 (de) 1992-12-11 1994-06-16 Teves Gmbh Alfred Geräuschreduziertes Pumpenaggregat, insbesondere für geregelte Bremsanlagen
CN2391030Y (zh) * 1999-08-30 2000-08-09 杭州大路实业有限公司 偏心滑块行程调节机构
JP2003214491A (ja) 2002-01-23 2003-07-30 Hitachi Unisia Automotive Ltd ポンプ装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009083290A1 *

Also Published As

Publication number Publication date
WO2009083290A1 (fr) 2009-07-09
CN101903225B (zh) 2013-06-19
CN101903225A (zh) 2010-12-01
DE102007062031A1 (de) 2009-06-25

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