WO2002008604A1 - Pompe a piston - Google Patents

Pompe a piston Download PDF

Info

Publication number
WO2002008604A1
WO2002008604A1 PCT/DE2001/002667 DE0102667W WO0208604A1 WO 2002008604 A1 WO2002008604 A1 WO 2002008604A1 DE 0102667 W DE0102667 W DE 0102667W WO 0208604 A1 WO0208604 A1 WO 0208604A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
pump
valve
inlet valve
stroke
Prior art date
Application number
PCT/DE2001/002667
Other languages
German (de)
English (en)
Inventor
Werner-Karl Marquardt
Wolfgang Schuller
Jürgen HAECKER
Rolf Stotz
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 WO2002008604A1 publication Critical patent/WO2002008604A1/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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0073—Piston machines or pumps characterised by having positively-driven valving the member being of the lost-motion type, e.g. friction-actuated members, or having means for pushing it against or pulling it from its seat
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/102—Disc valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/127—Disc valves

Definitions

  • the invention relates to a piston pump with the features of the preamble of claim 1.
  • the piston pump is in particular for use in a hydraulic, having a slip control device
  • Vehicle brake system provided.
  • Piston pumps of this type are known per se. They have a pump piston, which can be driven, for example, by means of an eccentric to a stroke movement, a complete stroke of the pump piston comprising a delivery stroke and a return stroke. During the delivery stroke, the pump piston reduces the volume of a working area of the piston pump and displaces fluid to be delivered from the working area. During the return stroke, the pump piston increases the volume of the work space and fluid flows into the work space. To control a fluid flow through the piston pump, the known piston pumps usually have an inlet valve and an outlet valve, which are often designed as check valves that are opened by a pressure difference in a flow direction.
  • the inlet valve of such a piston pump opens at the beginning of the return stroke of the pump piston and closes at the end of the return stroke.
  • the inlet valve would therefore be open during almost the entire return stroke and thus during approximately 50% of the total stroke movement of the pump piston.
  • the lifting movement includes the return stroke and the conveying stroke.
  • the opening time of the inlet valve is shorter, since a sufficient pressure difference has to be established at the inlet valve to open the inlet valve, for which purpose a piston travel in the direction of the return stroke is required.
  • the inlet valve is designed as a spring-loaded check valve
  • the return stroke length increases until the inlet valve opens, since a closing force of a valve closing spring of the inlet valve has to be overcome, as a result of which the pressure difference required to open the inlet valve increases.
  • the inlet valve of known piston pumps closes before the end of the return stroke, since a speed of the pump piston at the end of the return stroke and thereby also a pressure difference acting on the inlet valve in the opening direction is reduced and the valve closing spring closes the inlet valve before the end of the return stroke.
  • the actual opening duration of the inlet valve can be approximated to the theoretical value of 50% of the total stroke movement of the pump piston, but the value of 50% cannot be achieved. Because the friction acting on the valve closing body can only be set very inaccurately, there is a large scatter in the actual opening time of the inlet valve.
  • the invention takes a different path, it sets at the other reversal point of the pump piston, ie at the end of the return stroke and at the beginning of the delivery stroke on,
  • the piston pump according to the invention with the features of claim 1 has a valve control for the inlet valve of the piston pump.
  • the valve control is designed as a positive control, it is effective in the area of an end of the return stroke of the pump piston and a start of the delivery stroke of the pump piston.
  • the valve control of the piston pump according to the invention forcibly keeps the inlet valve open from before the end of the return stroke of the pump piston beyond the reversal point of the pump piston to after the start of the delivery stroke of the pump piston.
  • the inlet valve at the end of the return stroke of the pump piston is open independently of a pressure difference effective at the inlet valve and does not close prematurely when the pressure difference effective at the inlet valve decreases towards the end of the return stroke of the pump piston.
  • the valve control of the piston pump according to the invention keeps the inlet valve open beyond the end of the return stroke of the pump piston, as a result of which the opening period of the inlet valve is longer and can in principle even be extended to over 50% of the total stroke movement of the pump piston.
  • the percentage Opening time can be seen as a ratio to the stroke movement of the pump piston comprising the delivery stroke and the return stroke.
  • the longer opening time of the inlet valve has the advantage of a better filling of the working space of the piston pump and thus a higher delivery rate and a better efficiency.
  • Another advantage of the inlet valve which is forcibly opened at the end of the return stroke of the pump piston is that no pressure difference is required to keep the inlet valve open, which reduces the flow resistance of the inlet valve.
  • the piston pump according to the invention has the advantage of being easier to fill: slip-controlled vehicle brake systems have a large number of cavities due to piston pumps, solenoid valves, hydraulic accumulators and damper chambers. In order to be able to fill the vehicle brake system with brake fluid without bubbles, the vehicle brake system must be evacuated before filling in order to avoid the inclusion of gas bubbles in the cavities of the vehicle brake system.
  • the inlet valve and the outlet valve of the piston pump are closed during the evacuation, the working area of the piston pump is not evacuated, with the result that there is air in the brake system after filling.
  • this can be avoided by moving the pump piston to the end of the return stroke for evacuation, so that the pump piston is fully extended and the working space of the piston pump has its greatest volume.
  • the inlet valve is forcibly opened and the working space of the piston pump is evacuated together with the rest of the brake system.
  • the pump piston can also be driven to its lifting movement during the evacuation of the vehicle brake system, so that the inlet valve is forcibly opened at least temporarily, which is also a reliable evacuation of the working area of the piston pump during the evacuation of the brake system.
  • the simplified ability to fill the vehicle brake system according to the invention is also advantageous when the brake fluid is changed.
  • a valve closing spring of the inlet valve of the piston pump according to the invention is supported on a piston-fixed spring holder.
  • This has the advantage that a closing force of the valve closing spring is independent of the stroke position of the piston.
  • the closing force of the valve closing spring in this embodiment of the invention is the same over the entire piston stroke and is not greater at one reversal point of the pump piston than at the other.
  • Another advantage of this embodiment of the invention is that the valve closing spring can be made short, thereby preventing the valve closing spring from buckling when it is designed as a compression spring.
  • the pump piston of the piston pump according to the invention is designed as a stepped piston.
  • the pump piston is surrounded by an annular space in the pump housing, the volume of which decreases during the return stroke of the pump piston and increases during the delivery stroke of the pump piston.
  • the increase in the volume of the annular space surrounding the stepped piston during the delivery stroke causes a suction of fluid from an inlet of the piston pump during the delivery stroke.
  • the volume of the annular space surrounding the pump piston decreases, but at the same time the volume of the working space increases, the increase in volume of the working space being greater than the decrease in volume of the annular space, so that the piston pump also draws in fluid during the return stroke.
  • the piston pump according to the invention is provided in particular as a pump in a brake system of a vehicle and is used to control the pressure in wheel brake cylinders.
  • ABS or ASR or FDR or EHB are used for such brake systems.
  • the pump is used, for example, to return brake fluid from a wheel brake cylinder or from several wheel brake cylinders to a master brake cylinder (ABS) and / or to convey brake fluid from a reservoir into a wheel brake cylinder or into several wheel brake cylinders (ASR or FDR or EHB) ,
  • ABS master brake cylinder
  • ASR or FDR or EHB brake fluid from a reservoir into a wheel brake cylinder or into several wheel brake cylinders
  • the pump is required, for example, in a brake system with wheel slip control (ABS or ASR) and / or in a brake system (FDR) serving as a steering aid and / or in an electro-hydraulic brake system (EHB).
  • the wheel slip control can, for example, prevent the vehicle's wheels from locking during braking when the brake pedal (ABS) is pressed hard and / or the vehicle's driven wheels spinning when the accelerator pedal (ASR) is pressed hard ,
  • brake pressure is built up in one or more wheel brake cylinders regardless of whether the brake pedal or accelerator pedal is actuated, for example, to prevent the vehicle from breaking out of the lane desired by the driver.
  • the pump can also be used with an electro-hydraulic brake system (EMS) in which the pump conveys the brake fluid into the wheel brake cylinder or into the wheel brake cylinder if an electric brake pedal sensor detects an actuation of the brake pedal or if the pump serves to fill a memory of the brake system,
  • EMS electro-hydraulic brake system
  • Figure 1 shows an axial section of a piston pump according to the invention
  • Figure 2 shows a modified embodiment of a piston pump according to the invention compared to Figure 1.
  • the piston pump 10 according to the invention shown in the drawing is arranged in a hydraulic block of a vehicle brake system, which is not otherwise shown, and has a slip control device.
  • the hydraulic block forms a pump housing 12 of the piston pump 10 and will be referred to as such below.
  • further hydraulic components such as solenoid valves, hydraulic accumulators and damper chambers of the vehicle brake system are accommodated and hydraulically interconnected.
  • a stepped pump bore 14 is made, in which a pump piston 16 is received in an axially displaceable manner.
  • the pump piston 16 is designed here as a stepped piston.
  • the pump piston 16 On a section with a smaller diameter, the pump piston 16 is enclosed by an annular space 18 within the pump bore 14. A volume of the annular space 18 changes during a stroke movement of the pump piston 16; the volume of the annular space 18 increases during a delivery stroke and decreases during a return stroke of the pump piston 16. During the delivery stroke, the pump piston 16 moves downward in the drawing.
  • the pump piston 16 delimits a working space 20 of the piston pump 10 within the pump bore 14.
  • a volume of the working space 20 decreases during the delivery stroke and increases during the return stroke of the pump piston 16. Due to the change in volume of the working space 20 during the stroke movement of the pump piston 16 promotes the piston pump 10 according to the invention in a manner known from piston pumps, which is brake fluid in the exemplary embodiment.
  • the pump bore 14 and thus the working chamber 20 are closed with a sealing plug 22, which is held in a pressure-tight manner in an opening of the pump bore 14 by a circumferential caulking 24 of the material of the pump housing 12.
  • a sealing plug 22 which is held in a pressure-tight manner in an opening of the pump bore 14 by a circumferential caulking 24 of the material of the pump housing 12.
  • Piston return spring 26 arranged.
  • the piston return spring 26 is as
  • Front side of the pump piston 16 is arranged.
  • Pump piston 16 in a stroke position at the end of the return stroke and at the beginning of the delivery stroke, the pump piston 16 is located in the drawing at a reversal point. In this stroke position of the pump piston 16, the volume of the working space 20 is at a maximum.
  • an inlet bore 30 is provided in the pump housing 12, which opens radially into the annular space 18 of the pump bore 14. Brake fluid passes from the annular space 18 through a transverse bore 32 of the pump piston 16 into a blind hole 34 which is axially arranged in the pump piston 16 and which leads from the transverse bore 32 to the working space 20 of the piston pump 10.
  • a valve seat 36 of an inlet valve 38 of the piston pump 10 according to the invention is provided on the end face of the pump piston 16 facing the working chamber 20.
  • the inlet valve 38 is designed as a spring-loaded check valve.
  • the valve closing body 40 the inlet valve 38 has a valve disk in the form of a circular disk, which is pressed in the direction of the valve seat 36 by a valve closing spring 42 designed as a helical compression spring.
  • the valve closing body 40 can also have other shapes, for example spherical.
  • the pump piston 16 has at its end facing the working space 20 a hollow cylindrical collar 44 which surrounds the valve closing body 40.
  • the collar 44 has a larger diameter than the valve closing body 40, so that when the inlet valve 38 is open, brake fluid can flow from the blind hole 34 between the valve closing body 40 and the collar 44 into the working space 20 of the piston pump 10.
  • a valve stem 46 is formed on the valve closing body 40 and projects from a side of the valve closing body 40 facing away from the pump piston 16.
  • the valve stem 46 passes through a retainer 48, which is a cup-shaped
  • Retainer 48 is arranged in the working space 20 on the sealing plug 22, with an open side of the cup-shaped retainer 48 facing the sealing plug 22. 48 at its open side, the 'retainer has a radially outwardly extending flange 50 which presses against the plunger return spring 26 and thereby maintains in contact with the sealing plug 22 the retainer 48th
  • a bottom of the cup-shaped retainer 48 is provided with a center hole 52 through which the valve stem 46 passes.
  • the center hole 52 has an oversize with respect to the valve stem 46, so that the valve stem 46 is displaceable in the center hole 52.
  • the valve closing spring 42 surrounds the valve stem 46, it is supported on the bottom of the retainer 48 and presses the valve closing body 40 in the direction of the valve seat 36.
  • the valve stem 46 has a radially projecting head 54.
  • the head 54 is located within the retainer 48 on a side of the bottom of the retainer 48 facing away from the pump piston 16.
  • a diameter of the head 54 is larger than a diameter of the central hole 52 in the bottom of the retainer 48, so that the head 54 is the bottom of the retainer 48 engages behind.
  • a length of the valve stem 46 and a height of the retainer 48 are dimensioned such that the head 54 bears against the bottom of the retainer 48 at the reversal point of the pump piston 16, that is to say at the end of the return stroke and at the beginning of the delivery stroke, and the valve closing body 40 is shown as shown against the force of the valve spring 42 from the valve seat 36.
  • Retainer 48 thus keeps inlet valve 38 open via head 54 and valve stem 46 when pump piston 16 is at the reversal point shown.
  • the retainer 48, the head 54 and the valve stem 46 form a valve control 56 which controls the inlet valve 38 from before the end of the return stroke via the reversal point of the pump piston 16 forcibly keeps open until after the start of the delivery stroke.
  • An annular surface of the head 54 facing the bottom of the retainer 48 forms a retaining surface 58 of the valve closing body 40.
  • the bottom of the retaining 48 forms a counter surface 60 for the retaining surface 58 of the valve closing body 40.
  • the retaining surface 58 engages the counter surface 60.
  • the valve closing body 40 is lifted off the valve seat 36 and the inlet valve is kept open 38.
  • the pump piston 16 moves towards the valve closing body 40 of the inlet valve 38 until the valve closing body 40 is seated on the valve seat 36 and the inlet valve 38 closes.
  • the pump piston 16 takes along the valve closing body 40 seated on the valve seat 36 together with the valve stem 46 and the head 54.
  • the valve stem 46 moves into the cup-shaped retainer 48 and lifts the head 54 formed at the end of the valve stem 46 from the bottom of the retainer 48 forming the counter surface 60.
  • the piston pump 10 As the outlet valve 62, the piston pump 10 according to the invention has a spring-loaded check valve, which is shown as a symbol in the drawing and is arranged in an outlet bore 64, which is arranged radially to the pump bore 14 in the pump housing 12.
  • the illustrated stroke position of the pump piston 16 at the reversal point at the end of the return and start of the delivery stroke is assumed.
  • the rotatingly driven eccentric 28 presses the pump piston 16 into the working space 20, the pump piston 16 reducing the volume of the working space 20. This is the delivery stroke of the pump piston 16.
  • the rotating eccentric 28 presses the pump piston 16 with the valve seat 36 against the valve closing body 40 of the inlet valve 38, so that the inlet valve 38 closes shortly after the beginning of the delivery stroke.
  • valve closing body 40 moves with the pump piston 16, the inlet valve 38 remains closed and the pump piston 16 displaces brake fluid from the working space 20 through the outlet valve 62 and the outlet bore 64, i. h, the piston pump 10 delivers brake fluid.
  • the pump piston 16 moves back in the direction of the eccentric 28 as the eccentric 28 rotates further. This is the return stroke at which. the pump piston 16 increases the volume of the working space 20.
  • a pressure difference arises on the valve closing body 40, which lifts it against the force of the ' valve closing spring 42 from the valve seat 36, the inlet valve 38 is open, and brake fluid flows through the blind hole 34 in the pump piston 16 into the working space 20.
  • the annular space 18 created by the design of the pump piston 16 as a stepped piston and enclosing the pump piston 16 increases its volume during the delivery stroke of the pump piston 16. This increase in volume of the annular space 18 causes brake fluid to be sucked in through the inlet bore 30 during the delivery stroke. During the return stroke, it decreases Although the volume of the annular space 18, at the same time, however, the volume of the working space 20 increases, the increase in volume of the Working space 20 is larger due to its larger cross-sectional area.
  • the inlet valve 38 Since the inlet valve 38 is open during the return stroke, the working space 20 communicates with the annular space 18 through the blind hole 34 and the transverse bore 32 in the pump piston 16, and overall brake fluid is also sucked in through the inlet bore 30 during the return stroke of the pump piston 16.
  • the design of the pump piston 16 as a stepped piston thus has the advantage that brake fluid is sucked in during the entire stroke movement of the pump piston 16, which includes both the delivery stroke and the return stroke. In this way, the forced opening of the inlet valve 38 by the valve control 56 at the reversal point of the pump piston 16 at the end of the return and start of the delivery stroke is used for the inflow of brake fluid into the working space 20 until the inlet valve 38 closes shortly after the start of the delivery stroke. As a result, good filling of the working space 20 and high efficiency of the piston pump 10 are achieved.
  • the piston pump 10 according to the invention shown in FIG. 2 is designed in the region of the valve seat 36 of the inlet valve 38 and the valve closing spring 42 differently from the piston pump 10 shown in FIG. 1.
  • the piston pump 10 shown in FIG. 2 has a cup-shaped spring holder 66, which on the front side of the pump piston facing the working chamber 20
  • the spring holder 66 faces the pump piston 16.
  • the pump piston 16 has an annular step 68 with which it engages in the open side of the cup-shaped spring holder 66 and thereby holds it centered on the pump piston 16.
  • the spring holder 66 has a radially outwardly projecting flange 70 on its open side, against which the piston return spring 26 presses. In this way, the piston return spring 26 holds the spring holder 66 on the pump piston 16. Furthermore the flange 70 holds a sealing ring 72 and a guide ring 74 in position on the pump piston 16.
  • a bottom 76 of the cup-shaped spring holder 66 is provided with a center hole 78 which is penetrated by the valve stem 46 with play.
  • the valve closing body 40 is received in the spring holder 66 and is guided by the latter, so that the collar 44 of the pump piston 16 shown in FIG. 1 is omitted in the piston pump 10 according to FIG. 2.
  • An inner diameter of the cup-shaped spring holder 66 is larger than a diameter of the valve closing body 40, so that when the inlet valve 38 is open, brake fluid can flow around the valve closing body 40 into the working space 20 of the piston pump 10.
  • the valve closing spring 42 of the inlet valve 38 of the piston pump 10 shown in FIG. 2 is arranged in the cup-shaped spring holder 66.
  • the valve closing spring 42 is supported on the bottom 76 of the spring holder 66 and presses the valve closing body 40 in the direction of the valve seat 36 formed on the pump piston 16.
  • the valve closing spring 42 of the piston pump 10 shown in FIG. 2 is supported on the piston-fixed spring holder 66 , a closing force exerted on the valve closing body 40 by the valve closing spring 42 is independent of the stroke position of the pump piston 16.
  • a further advantage of the spring holder 66 is the axially short valve closing spring 42 which is possible as a result and in which there is no risk of buckling.
  • piston pump 10 shown in FIG. 2 is of the same design as the piston pump 10 shown in FIG. 1, and in order to avoid repetition, reference is made to the comments on FIG. 1. Corresponding reference numbers are used in FIGS. 1 and 2 for identical components.

Abstract

L'invention concerne une pompe (10) à piston pour un système de freinage hydraulique anti-patinage pour véhicules. Cette invention a pour objectif de parvenir à une grande durée d'ouverture d'une soupape d'admission (38) de cette pompe (10) à piston, laquelle soupape est conçue sous la forme d'un clapet anti-retour à ressort de rappel. A cet effet, une commande de soupape (56) est équipée d'un dispositif de retenue (48) conçu pour retenir un corps de fermeture (40) de la soupape d'admission (38) avant la fin d'une course de retour du piston (16) de pompe et pour ainsi maintenir la soupape d'admission (38) ouverte jusqu'au début d'une course d'alimentation du piston (16) de pompe. Une durée d'ouverture de la soupape d'admission (38) est ainsi allongée au delà d'un point mort bas du piston (16) de pompe. Cette pompe (10) à piston est de préférence conçue sous la forme d'une pompe à piston différentiel.
PCT/DE2001/002667 2000-07-21 2001-07-17 Pompe a piston WO2002008604A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000135537 DE10035537A1 (de) 2000-07-21 2000-07-21 Kolbenpumpe
DE10035537.4 2000-07-21

Publications (1)

Publication Number Publication Date
WO2002008604A1 true WO2002008604A1 (fr) 2002-01-31

Family

ID=7649733

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2001/002667 WO2002008604A1 (fr) 2000-07-21 2001-07-17 Pompe a piston

Country Status (2)

Country Link
DE (1) DE10035537A1 (fr)
WO (1) WO2002008604A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103109088A (zh) * 2011-03-25 2013-05-15 爱信艾达株式会社 电磁泵

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005017283B3 (de) * 2005-04-14 2006-08-03 Lucas Automotive Gmbh Kolbenpumpe für eine Fahrzeugbremsanlage
SE531362C2 (sv) * 2005-06-20 2009-03-10 Oehlins Racing Ab Pumpanordning för bl a fram- och bakhjulsdriven motorcykel

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB509480A (en) * 1936-10-08 1939-07-17 Bernhard Bischof Pumping devices for displacing liquid of low viscosity
GB602612A (en) * 1945-07-24 1948-05-31 Prec Developments Co Ltd Improvements relating to valve arrangements in piston pumps
US3254607A (en) * 1963-11-26 1966-06-07 Air Reduction Pump for a boiling liquid
FR2181198A5 (fr) * 1972-04-17 1973-11-30 Step
DE3742824A1 (de) * 1987-12-17 1989-07-13 Bosch Gmbh Robert Pumpe
DE4131033A1 (de) * 1991-09-18 1993-03-25 Zahnradfabrik Friedrichshafen Radialkolbenpumpe
DE4136624A1 (de) * 1991-11-07 1993-05-27 Daimler Benz Ag Ventilgesteuertes verdraengeraggregat mit ventilausloesung
EP0913578A1 (fr) * 1997-10-30 1999-05-06 Robert Bosch Gmbh Pompe à piston radiale avec soupape d'évacuation
DE19816289A1 (de) * 1998-02-09 1999-08-12 Itt Mfg Enterprises Inc Druckventil, insbesondere für eine Kolbenpumpe

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB509480A (en) * 1936-10-08 1939-07-17 Bernhard Bischof Pumping devices for displacing liquid of low viscosity
GB602612A (en) * 1945-07-24 1948-05-31 Prec Developments Co Ltd Improvements relating to valve arrangements in piston pumps
US3254607A (en) * 1963-11-26 1966-06-07 Air Reduction Pump for a boiling liquid
FR2181198A5 (fr) * 1972-04-17 1973-11-30 Step
DE3742824A1 (de) * 1987-12-17 1989-07-13 Bosch Gmbh Robert Pumpe
DE4131033A1 (de) * 1991-09-18 1993-03-25 Zahnradfabrik Friedrichshafen Radialkolbenpumpe
DE4136624A1 (de) * 1991-11-07 1993-05-27 Daimler Benz Ag Ventilgesteuertes verdraengeraggregat mit ventilausloesung
EP0913578A1 (fr) * 1997-10-30 1999-05-06 Robert Bosch Gmbh Pompe à piston radiale avec soupape d'évacuation
DE19816289A1 (de) * 1998-02-09 1999-08-12 Itt Mfg Enterprises Inc Druckventil, insbesondere für eine Kolbenpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103109088A (zh) * 2011-03-25 2013-05-15 爱信艾达株式会社 电磁泵

Also Published As

Publication number Publication date
DE10035537A1 (de) 2002-01-31

Similar Documents

Publication Publication Date Title
EP1101035B1 (fr) Pompe a piston
EP1108141B1 (fr) Pompe a piston
EP1185794B1 (fr) Pompe a piston
EP0913578A1 (fr) Pompe à piston radiale avec soupape d'évacuation
EP0932762A1 (fr) Piston tubulaire produit par formage a froid et bouchon de fermeture pour une pompe a pistons radiaux
EP0958453B1 (fr) Pompe a piston
EP1090228B1 (fr) Pompe a piston
WO1999006706A1 (fr) Pompe a piston
DE10042369A1 (de) Kolbenpumpe
EP1082544B1 (fr) Pompe a piston
EP1090230B1 (fr) Pompe a piston
EP1089902B1 (fr) Pompe a piston
DE102014221097A1 (de) Kolbenpumpe
WO2002008604A1 (fr) Pompe a piston
DE19809592B4 (de) Kolbenpumpe
DE102013222949B4 (de) Kolbenpumpe
DE10049909A1 (de) Kolbenpumpe
DE19847471B4 (de) Kolbenpumpe
DE19918123A1 (de) Kolbenpumpe
DE19812043B4 (de) Kolbenpumpe
DE19732748A1 (de) Kolbenpumpe
DE19918121B4 (de) Kolbenpumpe
DE19747937A1 (de) Kolbenpumpe bzw. Bremsanlage mit Kolbenpumpe
DE3200930A1 (de) Hydraulische bremsanlage mit blockierschutzeinrichtung fuer fahrzeuge

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): JP KR US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR

121 Ep: the epo has been informed by wipo that ep was designated in this application
122 Ep: pct application non-entry in european phase
NENP Non-entry into the national phase

Ref country code: JP