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WO2006051066A1 - Groupe electro-hydraulique - Google Patents

Groupe electro-hydraulique Download PDF

Info

Publication number
WO2006051066A1
WO2006051066A1 PCT/EP2005/055792 EP2005055792W WO2006051066A1 WO 2006051066 A1 WO2006051066 A1 WO 2006051066A1 EP 2005055792 W EP2005055792 W EP 2005055792W WO 2006051066 A1 WO2006051066 A1 WO 2006051066A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
unit according
hydraulic
switching device
electrohydraulic unit
Prior art date
Application number
PCT/EP2005/055792
Other languages
German (de)
English (en)
Inventor
Dieter Dinkel
Albrecht Otto
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 WO2006051066A1 publication Critical patent/WO2006051066A1/fr

Links

Classifications

    • 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
    • F04B49/121—Lost-motion device in the driving mechanism
    • 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
    • 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
    • B60T8/404—Control of the pump unit
    • B60T8/4059—Control of the pump unit involving the rate of delivery
    • 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
    • F04B1/0408—Pistons
    • 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
    • F04B49/18—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 changing the effective cross-section of the working surface of the piston

Definitions

  • the invention relates to an electro-hydraulic unit for motor vehicles.
  • it may be an aggregate for the conversion of electrical energy into mechanical energy, which is used in a brake system with a device for controlling the brake and traction slip and optionally for driving dynamics control in a motor vehicle, so that functions such as ABS, ASR or ESP be enabled.
  • variable passenger cars in particular so-called SUVs (sports utility vehicles), to MPVs, to 7-seaters or, for example, preferably in the USA to so-called light trucks.
  • SUVs sport utility vehicles
  • MPVs to 7-seaters
  • light trucks A feature of all these vehicles is their increased mass, which requires increased brakes.
  • large-volume brakes have an increased volume of brake fluid - also due to elasticity.
  • the intake volume must be provided by the electrohydraulic unit to meet the above functionalities.
  • an essential task of a brake system is to prevent unwanted changes in position of a parked vehicle, in short to allow the so-called parking brake function.
  • the active energy for actuating or releasing the parking brake is muscular by a vehicle driver or mechatronic a motor-gear unit generates.
  • Such variants are associated with the disadvantage that they are either not very comfortable, or require additional units for energy conversion, namely an electromotive actuator with electronic control unit, which increases the cost of a brake system inappropriate.
  • electrohydraulic units relate to a so-called hydraulic parking brake (HPB).
  • HPB hydraulic parking brake
  • Such parking brake devices differ significantly from conventional Parkbremsaktuatorik comprising a wear-prone brake cable by an already existing engine-pump assembly builds up the hydraulic energy which acts on the pistons in the wheel brakes so that they are locked by means of a separate device in the tensioned state, thereby to maintain the park braking effect.
  • the electromechanically generated hydraulic pressure is effectively chambered in the wheel brakes, which achieves the desired braking effect. This makes it possible to dispense with a muscular operation of a parking brake or on an additional electromechanical transducer. A mere actuation of an electric actuator or switch is completely sufficient.
  • the piston is designed in several parts and comprises at least two synchronously movable part pistons, wherein the first part piston is associated with a first hydraulically effective Duchmesser, and wherein the second part piston is associated with the second hydraulically effective diameter.
  • the invention is based on the task of electrohydraulic units with respect to their capacity to better adapt to the varying requirements of modern passenger cars, but without unduly increasing the construction costs and in particular the size. Another object is to avoid the disadvantages mentioned, and to provide an electro-hydraulic unit, which allows a simple, robust and preferably purely mechanical way, a gradation of hydraulic power.
  • the electrohydraulic unit be provided with a device in order to switch easily between hydraulic surfaces of differing dimensions or effective surface combinations (Al, Al + A2) of a piston pump.
  • the advantage of the device according to the invention is that, for example, a first energy generation mode is based on a first active hydraulic surface (Al + A2) and a second energy generation mode is based on a second active hydraulic surface (A2), the first active surface (A1 + A2) greater than the second effective area (A2) is formed.
  • This makes it possible to promote high flow rates, for example, only in the low pressure range with a relatively large piston effective area Al + A2, and, for example, to switch suddenly or successively on the relatively small piston effective area Al from entry into the high pressure area.
  • the invention makes it possible to provide a targeted hydraulic gearshift, which is automatically initiated either by specific physical process variables or electronically controlled, on the basis of which the advantage that a motor, undersized compared to conventional power units, can even cope with peak loads without lasting damage to be overloaded. Needless to say, this measure may be associated with a reduction in the power of the required electric motor, as well as a reduction in cost, with the added benefit of reducing the amount of power consumed. So the invention leads to a reduction of the on-board network stress.
  • the invention is associated with the further advantage that the hydraulic switching is completely independent of an influence of a mechanical transmission such as in particular an eccentricity between the pump drive and the radial piston pump. Because the eccentricity remains constant.
  • a hydraulic parking brake can be quickly filled by using a delivery piston with a large hydraulic effective area with large flow rates, without having to make a change in the delivery stroke.
  • a reduced hydraulic effective area is provided for the supply of low flow rates in a high pressure area. Because the active surfaces are thus formed reducible targeted, this allows a reduction of the load of a pump drive motor and consequently a reduced electrical current consumption. The electrical stress on the vehicle electrical system is consequently reduced.
  • the invention is not bound to parking brake applications, but in principle can always be used when intelligent energy management is required. This allows further fields of application in order to open up new uses beyond braking and chassis control technology.
  • the piston pump comprises a device with which at least one piston is formed telescopic. This causes a change possibility for the displacement stroke.
  • the device is provided as a switching device to allow a relative movement between a first piston segment with a first hydraulically effective cross section and a second piston segment with a second hydraulically effective cross section, or to prevent. This makes it possible to bundle the hydraulically effective cross-sections in different combinations or to act individually.
  • the switching device is at least operatively, but preferably also locally, placed between the piston segments.
  • the piston segments have identically sized or differently sized hydraulic active surfaces.
  • the piston pump is designed as a radial piston pump, and has a first centric piston segment, which of a radial outer, concentric piston segment is surrounded.
  • the centric piston segment has a comparatively small hydraulic effective area (Al), while the large effective area is additively composed of the hydraulic effective areas (A1 + A2) of two piston segments.
  • the cross section of the piston segments - and thus also the effective surfaces - is circular or circular.
  • the switching in the composition of the active surfaces Al, A1 + A2 is hydraulically controlled due to the prevailing hydraulic pressure in a working space of the piston pump.
  • a radially outer, annular piston segment can be arranged by means of a transition fit frictionally engaged on the circumference of a central piston segment.
  • the centric piston segment is driven directly by the drive (eccentric).
  • the frictional engagement between the outer and inner piston segments is now tuned such that the radially outer piston segment only participates in the displacement movement in the low or medium pressure region.
  • the hydraulic pressure forces exceed the friction stresses between the two piston segments.
  • the radially outer piston segment only participates again in the displacement movement when the limiting pressure has fallen below.
  • the device comprises at least one elastomeric element, which yields under the action of a predetermined hydraulic pressure in a displacement chamber to allow a switch in the composition of the hydraulic active surfaces.
  • the switching device has a first elastomeric element which is suitable for urging the two piston segments into a rearward dead center position, while a second elastomeric element is intended to elastically bias one of the two piston segments against the action of the hydraulic pressure.
  • the switching device has at least one electromagnetically switchable element, which in order to activate or deactivate the clutch with an electronic controller is in communication to make the activation or deactivation using the electronic controller.
  • FIG. 1 is an enlarged section through a piston pump for use in a hydraulic unit, comprising a coupling device with a friction element, and
  • Fig. 2 shows an embodiment of the invention using a coupling device with an elastomer element
  • Fig. 3 is a schematic diagram to illustrate Wirwirambaenpsychon on piston segments.
  • a brake system usually includes a pneumatic brake booster, and one, a
  • Pressure medium reservoir having, master cylinder or simulator whose pressure chambers can be connected via brake lines with wheel brakes.
  • the pressure chambers and wheel brakes are combined in pairs in so-called brake circuits I, II.
  • brake circuits I, II the so-called diagonal distribution has been enforced by combining diagonally opposite wheel brakes of the front axle and rear axle of a vehicle, in principle, other divisions such as the so-called black / white division under pairwise combination of the wheel brakes of an axle is possible.
  • a pressure sensor for detecting a pressure applied by the driver in a connection between the pressure chamber and wheel brakes is usually a pressure sensor in the brake line, which connects a pressure chamber with wheel brakes from the brake circuit I.
  • a receiving body (HCU) 1 comprises the electromagnetic valves and essentially the hydraulic bore.
  • the receiving body forms a core of an electro-hydraulic unit.
  • Each brake circuit has an electromagnetic isolation valve and, for each wheel brake, one inlet valve and one outlet valve in each case.
  • II return lines are connected, which lead back to the respective master cylinder pressure chamber.
  • the exhaust valves are intended for targeted pressure reduction in the wheel brake.
  • at least one low-pressure accumulator is integrated in the return, which can absorb discharged fluid in a flash, if the pump delivery is delayed.
  • Each brake circuit has an electric motor driven piston pump 2, which sucks from the low pressure accumulator or from a brake fluid reservoir to - depending on the respective necessary function - to promote pressure chambers or in the wheel brakes.
  • each brake circuit I, II downstream between the low pressure accumulator and a schematically illustrated input E of the piston pump 2 each have a suction line into a suction channel.
  • an electromagnetically actuated changeover valve is used, For example, when active vehicle dynamics control establishes a pressure medium connection between the master brake cylinder, a brake fluid reservoir and the input E of the piston pump 2.
  • FIGS. 1 and 2 largely agree, matching features are provided with corresponding reference numerals. After explaining the common features and relationships will be discussed in connection with features of FIG.
  • a drive shaft 3 extends with one end into a crank chamber 4 in the receiving body 1, and rotates an eccentric 5, which from an eccentric bearing
  • a largely cylindrical pump cartridge 7 comprises at least one bushing section 8 and is mounted in a stepped bore 9 of the receiving body 1, which is closed by a cover 10. Input E and output A open into the stepped bore 9.
  • the piston 7 includes a segmented, partially hollow piston 11, which is arranged sealed and oscillatory movable in the pump cartridge 7.
  • the piston 11 is at one end to a bearing outer ring 12 of the eccentric 6, and another end protrudes into a displacement chamber 13 and has in this area a seat 14 for a check valve body 15.
  • a return spring 16 is between receiving body 1 and Clamp 11 is clamped, and serves the elastic bias of the piston 11 to return to the bottom dead center.
  • a - already described in parts - pressure valve 17 and a suction valve 18 is provided, which together the ventilation of the Displacement space 13 serve.
  • a special feature of the invention is that the piston 11 has a first, directly from the bearing outer ring 12 driven, central piston segment 19, which is necessarily taken along with each eccentric rotation. As a result, an effective hydraulic active surface Al is provided, which generally contributes to fluid delivery.
  • the central piston segment 19 essentially has a circular or annular cross section and is surrounded by a second, annular piston segment 20, which has a circular ring cross section and has the hydraulic effective area A2.
  • the active surfaces Al and A2 may have identical matching or different sized geometric surfaces.
  • a sealing element 21 is provided on the central piston segment 19.
  • this is provided with a sealing element 22.
  • a switching device may allow or prevent a relative movement between the piston segments 19, 20.
  • the switching device makes possible a kinematics in which either all the piston segments 19, 20 together with additive combined hydraulic active surface Al + A2, or only the central, positively driven piston segment 19 participate with its active surface Al on the conveying movement.
  • a contact surface between the central piston segment 19 and the radially outer piston segment 20 which is tolerated so that a frictional entrainment the indirectly entrained radially outer piston segment 20 takes place only in the low and medium pressure range.
  • the switching device is thereby effective between the piston segments 19,20. After exceeding a certain limit pressure in the displacement chamber 13 solves the
  • Switching device in a sense automatically automatically the force or frictional engagement between the piston segments 19,20.
  • the radially outer piston segment 20 remains as it were, and only the positively driven, central, radially inner piston segment 19 participates in the displacement.
  • Fig. 2 illustrates two different dead centers of another embodiment of the invention.
  • the switching device has Elasto elite, which allow a switching operation.
  • a first elastomeric element - in the form of a known prior art return spring 16 - acts on the two piston segments 19,20 directly or indirectly in the direction of the eccentric 5.
  • the radially inner piston segment 19 is always placed back in a bottom dead center and held in contact with the eccentric 5 ( lower half of the figure).
  • a stop 23 is defined for the radially outer piston segment 20.
  • a second elastomer element 24 counteracts the restoring spring 16 and urges the radially outer piston segment 20 against the action of the hydraulic pressure in the displacement chamber 13. As a result, this piston segment 20 is held in elastic contact with the stop 23 in principle with a defined preloading force.
  • the stopper 23 is provided on a component, which at the same time as a spring plate for the support of Return spring 16 on the central piston segment 19 is used.
  • the second elastomeric element 24 is provided to yield under a predetermined hydraulic pressure such that the frictional connection between the two piston segments 19, 20 is made possible or canceled.
  • the second elastomeric element 24 is designed as an elastically prestressed helical spring, which is supported on the radially outer piston segment 20 on the one hand and on the shoulder 26 of the pumping cartridge 7 on the other hand.

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)

Abstract

La présente invention concerne un groupe électro-hydraulique, en particulier un dispositif pour réguler le glissement de freinage et d'entraînement et pour réguler la dynamique de freinage. L'invention a pour objet de mettre à disposition un groupe électro-hydraulique qui permet de manière simple l'existence de plusieurs modes de production d'énergie. A cet effet, le groupe électro-hydraulique comprend une pompe à piston (2) et un dispositif qui sert à effectuer la commutation entre différentes surfaces hydrauliques actives ou combinaisons de surfaces hydrauliques actives (A1; A1+A2).
PCT/EP2005/055792 2004-11-12 2005-11-07 Groupe electro-hydraulique WO2006051066A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102004054899 2004-11-12
DE102004054899.4 2004-11-12
DE102005034571.9 2005-07-22
DE102005034571A DE102005034571A1 (de) 2004-11-12 2005-07-22 Elektrohydraulisches Aggregat

Publications (1)

Publication Number Publication Date
WO2006051066A1 true WO2006051066A1 (fr) 2006-05-18

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ID=35520542

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/055792 WO2006051066A1 (fr) 2004-11-12 2005-11-07 Groupe electro-hydraulique

Country Status (2)

Country Link
DE (1) DE102005034571A1 (fr)
WO (1) WO2006051066A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7690899B2 (en) 2007-06-18 2010-04-06 Advics Co., Ltd. Piston pump
GB2476157A (en) * 2009-12-10 2011-06-15 Bosch Gmbh Robert Piston pump for a hydraulic vehicle brake system

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009021966A1 (de) 2009-05-19 2010-11-25 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102010001237B4 (de) 2009-12-01 2024-09-12 Continental Automotive Technologies GmbH Verfahren zur Montage eines Federanschlags einer Kolbenrückstellfeder mittels eines Rastmechanismus an einem Pumpenkolben einer Kolbenpumpe
DE102010002283A1 (de) 2010-02-24 2011-08-25 Continental Teves AG & Co. OHG, 60488 Kolbenpumpe
DE102010028539A1 (de) 2010-05-04 2011-11-10 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102011004283A1 (de) 2011-02-17 2012-08-23 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102011081777A1 (de) 2011-08-30 2013-02-28 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102012207000A1 (de) 2012-04-27 2013-10-31 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102012218585A1 (de) 2012-10-12 2014-04-17 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102012221035A1 (de) 2012-11-19 2014-05-22 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102013200548A1 (de) 2013-01-16 2014-07-17 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102014213844A1 (de) 2014-07-16 2016-01-21 Continental Teves Ag & Co. Ohg Kolbenpumpe

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1148819A (fr) * 1956-02-27 1957-12-16 Pompe perfectionnée
US3112705A (en) * 1961-10-05 1963-12-03 Jane Wallen Two-speed hydraulic pumps
DE2101037A1 (de) * 1971-01-11 1972-07-27 Glaubitz, Peter Elvier, 8070 Ingolstadt Selbstregelnde Kolbenpumpe
US3775027A (en) * 1971-10-01 1973-11-27 Gray Manuf Co Inc Two-speed pump
WO1989008573A2 (fr) * 1988-03-08 1989-09-21 Alfred Teves Gmbh Systeme de freinage
WO1997029292A2 (fr) * 1996-02-09 1997-08-14 Itt Manufacturing Enterprises, Inc. Systeme combine de frein de service et de frein de stationnement
WO1999023387A1 (fr) * 1997-10-30 1999-05-14 Robert Bosch Gmbh Pompe a piston
WO2001055595A1 (fr) * 2000-01-25 2001-08-02 Continental Teves Ag & Co. Ohg Pompe a piston

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1148819A (fr) * 1956-02-27 1957-12-16 Pompe perfectionnée
US3112705A (en) * 1961-10-05 1963-12-03 Jane Wallen Two-speed hydraulic pumps
DE2101037A1 (de) * 1971-01-11 1972-07-27 Glaubitz, Peter Elvier, 8070 Ingolstadt Selbstregelnde Kolbenpumpe
US3775027A (en) * 1971-10-01 1973-11-27 Gray Manuf Co Inc Two-speed pump
WO1989008573A2 (fr) * 1988-03-08 1989-09-21 Alfred Teves Gmbh Systeme de freinage
WO1997029292A2 (fr) * 1996-02-09 1997-08-14 Itt Manufacturing Enterprises, Inc. Systeme combine de frein de service et de frein de stationnement
WO1999023387A1 (fr) * 1997-10-30 1999-05-14 Robert Bosch Gmbh Pompe a piston
WO2001055595A1 (fr) * 2000-01-25 2001-08-02 Continental Teves Ag & Co. Ohg Pompe a piston

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7690899B2 (en) 2007-06-18 2010-04-06 Advics Co., Ltd. Piston pump
GB2476157A (en) * 2009-12-10 2011-06-15 Bosch Gmbh Robert Piston pump for a hydraulic vehicle brake system
FR2953890A1 (fr) * 2009-12-10 2011-06-17 Bosch Gmbh Robert Pompe a piston pour une installation hydraulique de freins de vehicules

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