EP1362187A1 - Pompe a piston - Google Patents

Pompe a piston

Info

Publication number
EP1362187A1
EP1362187A1 EP02708221A EP02708221A EP1362187A1 EP 1362187 A1 EP1362187 A1 EP 1362187A1 EP 02708221 A EP02708221 A EP 02708221A EP 02708221 A EP02708221 A EP 02708221A EP 1362187 A1 EP1362187 A1 EP 1362187A1
Authority
EP
European Patent Office
Prior art keywords
pump
piston
piston ring
ring
bore
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Withdrawn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
EP02708221A
Other languages
German (de)
English (en)
Inventor
Ernst-Dieter Schaefer
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 EP1362187A1 publication Critical patent/EP1362187A1/fr
Withdrawn legal-status Critical Current

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
    • 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
    • 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
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/143—Sealing provided on the piston

Definitions

  • the invention relates to a piston pump with the features of the preamble of claim 1.
  • the piston pump is provided in particular for conveying brake fluid in a hydraulic vehicle brake system.
  • Piston pumps of this type are known in a large number of configurations.
  • An example of such a piston pump for a hydraulic vehicle brake system is disclosed in DE 197 12 147 A1.
  • the known piston pump has a pump housing with a pump bore in which a pump piston lies axially displaceably.
  • the pump piston can be driven, for example by means of an eccentric, for a stroke movement that reciprocates axially in the pump bore.
  • An axial section of the pump bore forms a pump chamber of the piston pump, the volume of which is alternately increased (return stroke) and reduced (delivery stroke) during the stroke movement of the pump piston.
  • the piston pump delivers fluid (brake fluid) in a manner known per se.
  • the pump piston of the known piston pump has a guide ring.
  • a sealing ring is provided on a side of the guide ring facing the pump chamber.
  • the piston pump according to the invention with the features of claim 1 has a piston ring on a side of the pump piston facing the pump chamber, which seals the pump piston in any case during the delivery stroke in the pump bore and which axially displaceably guides the pump piston in the pump bore at the end facing the pump chamber.
  • the piston ring of the piston pump according to the invention thus forms both a sealing ring and a guide ring on the side of the pump piston facing the pump chamber. It is sufficient if the piston ring seals the pump piston in the pump bore during the delivery stroke; a seal is not necessary during the return stroke of the pump piston.
  • the piston ring can, for example, have a sealing sleeve which can be flowed over during the return stroke of the pump piston in the direction of the pump chamber.
  • the piston ring can be held axially on the pump piston or in the pump bore, ie the piston ring can move with the pump piston or be held stationary in the pump bore.
  • the invention has the advantage that a single piston ring on the side of the pump piston facing the pump chamber is sufficient for its axial guidance and sealing in the pump bore.
  • the manufacturing and assembly costs are reduced.
  • an axial length required for sealing and axially guiding the pump piston through the Use of only one piston ring reduced, the pump piston and the piston pump can be made axially shorter.
  • the piston ring has in an axial section a circumferential surface which is acted upon by fluid from the pump chamber.
  • the axial section preferably faces the pump chamber.
  • the purpose of this embodiment of the invention is that the pressurized fluid during the delivery stroke of the pump piston in the pump chamber under pressure applied to the piston ring in the axial section on the peripheral surface ', and thereby the piston ring presses facing away from mating surface on one of the applied circumferential surface of the piston ring to form a good seal. to reach the pump piston during the delivery stroke.
  • the counter surface against which the fluid from the pump chamber presses the piston ring is a wall of the pump bore, along which the piston ring slides during the stroke movement of the pump piston.
  • the peripheral surface acted upon by the fluid is an inner peripheral surface of the piston ring.
  • the circumferential surface is limited to an axial section of the piston ring, since the piston ring lies sealingly against the pump piston over a further part of its axial length and is not acted upon by fluid.
  • the counter surface against which the fluid from the pump chamber seals the piston ring during the delivery stroke is an outer peripheral surface of the pump piston, which in this case slides axially in the piston ring.
  • the peripheral surface acted upon by the fluid from the pump chamber during the delivery stroke of the pump piston is in this case an outer peripheral surface of the piston ring.
  • Claim 3 provides that the circumferential surface acted upon by the fluid from the pump chamber by changing the diameter of the piston ring on the inside or outside. on the outer circumference of the piston ring.
  • the change in diameter can be represented, for example, as a conical surface (claim 4) or as a ring step (claim 5) on the inner or outer circumference of the piston ring.
  • This configuration has the advantage that there is no need to change the diameter of the pump piston and / or the pump bore in the region of the piston ring in order to apply fluid from the pump chamber to the piston ring in an axial section. This simplifies and reduces the cost of producing the pump piston or the pump bore.
  • the piston ring is formed symmetrically to a radial center plane, so it has the change in diameter to show the circumferential surface acted upon by the fluid from the pump chamber on its two end faces.
  • claim 7 provides an undersize of an inner diameter of the piston ring in relation to the pump piston and / or claim 8 an oversize of an outer diameter of the piston ring in relation to the pump bore.
  • the undersize or oversize causes the pump piston to bear against the pump piston or in the pump bore with pretension.
  • a free area is provided over part of an axial length of the piston ring, so that the piston ring is only in contact with the pump bore or the pump piston over part of its axial length.
  • the free area reduces friction of the piston ring.
  • the free surface is provided axially outside the circumferential surface of the piston ring acted upon by the fluid from the pump chamber.
  • 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, ASR or FDR or EHB are comparable for such brake systems, applies.
  • 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 independently of an actuation of the brake pedal or accelerator pedal, for example in order to prevent the vehicle from breaking out of the lane desired by the driver.
  • the pump can also be used in an electrohydraulic brake system (EMS), in which the pump delivers the brake fluid into the wheel brake cylinder or in the wheel brake cylinders if an electric brake pedal sensor detects an actuation of the brake pedal or the pump for filling a memory of the brake system serves.
  • EMS electrohydraulic brake system
  • FIG. 1 shows a piston pump according to the invention in axial section
  • FIG. 2 shows an enlarged illustration of a piston ring of the piston pump from FIG. 1 according to detail II in FIG. 1;
  • Figures 3 and 4 two modified embodiments of piston rings of the piston pump of Figure 1 in a representation corresponding to Figure 2.
  • the piston pump 10 according to the invention shown in FIG. 1 is inserted into a stepped pump bore 12 which is mounted in a hydraulic block which forms a pump housing 14.
  • the hydraulic block of which only one fragment surrounding piston pump 10 is shown in the drawing, is part of a slip-controlled hydraulic vehicle brake system, which is not shown in the drawing.
  • further hydraulic components such as solenoid valves or pressure accumulators are inserted into it and hydraulically connected to one another and to the piston pump 10 according to the invention.
  • the piston pump 10 has a pump piston 16, one end of which, facing away from a pump chamber 18, is guided with a guide ring 20 in the pump bore 12 and sealed with a sealing ring 22.
  • the pump chamber 18 is an axial section of the pump bore 12 at one end of the pump piston 16.
  • a volume of the pump chamber 18 changes during a stroke movement of the pump piston 16, as a result of which the piston pump 10 conveys fluid in a manner known per se.
  • Another end of the piston 16 facing the pump chamber 8 is guided and sealed axially displaceably with a piston ring 24 to be explained in a bushing 26 of the piston pump 10.
  • the bushing 26 is press-fitted into the pump bore 12 of the pump housing 14. The press fit creates a seal between the inlet and outlet side, ie between the low and high pressure side of the piston pump 10.
  • an axial blind bore 28 is made in the piston 16 from a side facing the pump chamber 18, which is close to it
  • a check valve is attached as an inlet valve 36 on a side of the piston 16 facing the pump chamber 18.
  • the inlet valve 36 has a valve ball 38 as a valve closing body which interacts with a conical valve seat 40 which is attached to an opening of the blind bore 28 of the piston 16.
  • a helical compression spring as a valve closing spring 42 presses the valve ball 38 against the valve seat 40.
  • the valve ball 38 and valve closing spring 42 are accommodated in a valve cage 44, which is made as a cup-shaped deep-drawn part made of sheet metal with a diameter approximately corresponding to the diameter of the piston 16 and is provided with throughflow openings 46.
  • the valve cage 44 has an annular step 48, with which it rests on an end face of the piston 16 facing the pump chamber 18.
  • valve cage 44 has a radial flange 50, which is integral with it, and against which a helical compression spring acts as a piston return spring 52 and in this way holds the valve cage 44 on the piston 16.
  • the radial flange 50 also holds the piston ring 24 between itself and a support ring 56, which is supported on an annular shoulder 54 of the piston 16, on the piston 16 in the axial direction.
  • the piston return spring 52 presses the piston 16 in the axial direction against a circumference of an electric motor via the radial flange 50 of the valve cage 44 Eccentric 58 which can be driven in rotation and which serves to drive the piston 16 for a reciprocating stroke movement in a manner known per se.
  • the bushing 26 On a side adjoining the pump chamber 18, the bushing 26 has a bushing base 60 which is integral with it and in the middle of which a through-hole 62 of the piston pump 10 is made.
  • a closure part 64 is attached to the liner bottom 60.
  • the closure part 64 has the shape of a cylindrical stopper. It is inserted into the pump bore 12 and fastened in the pump bore 12 by caulking 66 of the pump housing 14 and is sealed in a fluid-tight manner. The closure part 64 also holds the bushing 26 in the pump bore 12.
  • a flat, preferably cylindrical recess 68 is made in the closure part 64 on one end face facing the bushing 26, into which the bushing 26 with its bushing base 60 is inserted.
  • the bushing 26 has, on its bushing base 60 inserted in the closure part 64, an outwardly projecting radial collar 70 which forms an undercut 72 which is undercut by an edge 74 of the recess 68 of the closure part 64.
  • an edge 74 is undercut by an edge 74 of the recess 68 of the closure part 64.
  • Flanging at three to four points on the circumference is sufficient for fastening.
  • an axial blind hole 76 is made in the closure part 64, in which a check valve is accommodated as an outlet valve 78, which cooperates with a valve seat 80 which is attached to an opening of the outlet hole 62 in the liner bottom 60 facing the closure part 64.
  • a valve ball 82 is used as a valve closing body, which of a Helical compression spring 84 is pressed as a valve closing spring against the valve seat 80.
  • a number of radial channels 86 are attached in an outer side of the liner base 60, which open into an annular channel 88, which is attached to the bottom of the recess 68 of the closure part 64.
  • Outlet channels 90 lead outward from the ring channel 88 into a ring line 92 which surrounds the liner bottom 60 in the pump bore 12.
  • An outlet bore 94 which is made in the pump housing 14, opens into the ring line 92.
  • the piston ring 24 shown enlarged in FIG. 2 has a double function, it seals the pump piston 16 in the pump bore 12 in the pump housing 14 and it guides the piston 16 axially in the pump bore 12.
  • the piston ring 24 forms a sealing and guide ring.
  • the piston ring 24 is made of a plastic (PTFE, polytetraflurethylene).
  • the piston ring 24 has an undersize in relation to the pump piston 16, that is to say it is placed on the pump piston 16 with a prestress and thus in a sealing manner.
  • the piston ring 24 has an oversize, so that here too it rests with a prestress and thereby in a sealing manner.
  • the piston ring 24 is held axially between the support ring 56 and the radial flange 50 of the valve cage 44. There is axial play between the support ring 56 and the radial flange 50, the piston ring 24 is not preloaded axially. Since the piston ring 24 is held axially between the support ring 56 and the radial flange 50 on the piston 16, the piston ring 24 moves with the pump piston 16. During a stroke movement of the pump piston 16, the piston ring 24 slides along a wall of the pump bore 12, which forms a counter surface 96, against which the piston ring 24 rests.
  • the piston ring 24 can be reinforced with carbon fibers, for example. A graphite admixture can improve the sliding properties of the piston ring 24.
  • the piston ring 24 has an inner cone 98 on its end face facing the pump chamber 18.
  • the inner cone 98 extends over part of an axial length of the piston ring 24.
  • An outer surface of the inner cone 98 forms an inner circumferential surface 100 of the piston ring 24 which, since the inner cone 98 is open in the direction of the pump chamber 18, is acted upon by brake fluid from the pump chamber 18 .
  • the brake fluid pressurized by the pump piston 16 in the pump chamber 18 acts on the inner peripheral surface 100. of the piston ring 24 with pressure and thereby presses the piston ring 24 radially outward against the wall of the pump bore 12, which forms the counter surface 96.
  • the pressurization of the inner circumferential surface 100 ensures a reliable sealing of the pump piston 16 in the pump bore 12, in particular when the delivery pressure is high.
  • FIG 3 shows a development of the piston ring 24.
  • This piston ring has an annular step 102 on the outer circumference, through which a gap 104 is formed between the piston ring 24 and the peripheral wall of the pump bore 12.
  • the gap 104 is provided on a side of the piston ring 24 facing away from the pump chamber 18.
  • the gap 104 forms a free area that reduces the friction of the piston ring 24.
  • the free surface is provided axially outside the inner cone 98 of the piston ring 24 and does not reduce the sealing effect of the piston ring 24 due to the pressurization in the area of the inner cone 98.
  • FIG. 4 shows a further modification of the piston ring 24 from FIGS. 1 and 2.
  • the piston ring 24 shown in FIG. 4 has inner cones 98 on its two end faces.
  • the piston ring 24 is thereby symmetrical to its radial center plane and therefore cannot be placed on the piston 16 upside down.
  • This configuration rules out assembly errors of the piston ring 24.
  • the second inner cone 98 has no further meaning.
  • the piston 16 in FIG. 4 has a radial collar 106 which is integral with it and stands outwards for axially supporting the piston ring 24 on the pump piston 16. This eliminates the support 56.
  • a conical chamfer 108 of the pump piston 16 at the transition of the radial collar 106 into the pump piston 16 supports the piston ring 24 on the inner cone 98 on the side of the piston ring 24 facing away from the pump chamber 18 and thereby avoids an enlargement of the pressurized inner cone 98 on the side facing the pump chamber 18 Side of the piston ring 24 when the piston pump 10 is operating.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une pompe à piston (10) pour un système de freinage hydraulique de véhicule, à antipatinage. Selon l'invention, cette pompe à piston (10) présente un segment de piston (24) constitué par exemple de PTFE, servant aussi bien de segment d'étanchéité que de segment de guidage. L'invention permet de réduire la complexité de montage et les coûts de fabrication de la pompe à piston (10). L'objectif de l'invention est d'obtenir une étanchéification sûre. A cet effet, le segment de piston (24) présente un cône intérieur sur son côté opposé à une chambre de pompe (18) de sorte que, pendant la course de refoulement, ledit segment de piston (24) soit soumis à une pression provenant de la chambre de pompe (18) et soit plaqué de manière étanche contre un alésage de pompe (12).
EP02708221A 2001-02-12 2002-02-07 Pompe a piston Withdrawn EP1362187A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10106641 2001-02-12
DE10106641A DE10106641A1 (de) 2001-02-12 2001-02-12 Kolbenpumpe
PCT/DE2002/000447 WO2002064976A1 (fr) 2001-02-12 2002-02-07 Pompe a piston

Publications (1)

Publication Number Publication Date
EP1362187A1 true EP1362187A1 (fr) 2003-11-19

Family

ID=7673883

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02708221A Withdrawn EP1362187A1 (fr) 2001-02-12 2002-02-07 Pompe a piston

Country Status (5)

Country Link
US (1) US20030170133A1 (fr)
EP (1) EP1362187A1 (fr)
JP (1) JP2004518078A (fr)
DE (1) DE10106641A1 (fr)
WO (1) WO2002064976A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004056660A1 (de) * 2004-11-24 2006-06-01 Robert Bosch Gmbh Kolbenpumpe und Kolbenring
DE102004061810A1 (de) * 2004-12-22 2006-07-06 Robert Bosch Gmbh Kolbenpumpe mit wenigstens einem Stufenkolbenelement
DE102005017283B3 (de) * 2005-04-14 2006-08-03 Lucas Automotive Gmbh Kolbenpumpe für eine Fahrzeugbremsanlage
DE102006025027A1 (de) * 2006-05-26 2007-11-29 Robert Bosch Gmbh Kolbenpumpe
DE102009047217A1 (de) * 2009-11-27 2011-06-01 Robert Bosch Gmbh Kolbenplumpe
DE102014212292A1 (de) * 2014-06-26 2015-12-31 Robert Bosch Gmbh Auslassventil mit einem Aufnahmeelement

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US281579A (en) * 1883-07-17 Electric valve
US5012643A (en) * 1989-12-07 1991-05-07 Masanobu Higami Pressure-driven engine
DE4236682A1 (de) * 1992-10-30 1994-05-05 Teves Gmbh Alfred Hydraulische Hochdruckpumpe mit Überströmmanschette
DE19712147A1 (de) * 1996-09-19 1998-03-26 Bosch Gmbh Robert Kolbenpumpe
DE19747936A1 (de) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Kolbenpumpe
JP2001501274A (ja) * 1997-07-30 2001-01-30 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング ピストンポンプ
JP2000110737A (ja) * 1998-10-02 2000-04-18 Nissin Kogyo Co Ltd プランジャポンプ
DE19918122A1 (de) * 1999-04-22 2000-11-23 Bosch Gmbh Robert Kolbenpumpe
US6280162B1 (en) * 1999-06-02 2001-08-28 Virtual Data Security, Llc Radial piston pump
DE19924774A1 (de) * 1999-05-29 2000-11-30 Bosch Gmbh Robert Kolbenpumpe

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
None *
See also references of WO02064976A1 *

Also Published As

Publication number Publication date
JP2004518078A (ja) 2004-06-17
US20030170133A1 (en) 2003-09-11
DE10106641A1 (de) 2002-08-22
WO2002064976A1 (fr) 2002-08-22

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