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WO1999006702A1 - Pompe a piston - Google Patents

Pompe a piston Download PDF

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Publication number
WO1999006702A1
WO1999006702A1 PCT/DE1998/001308 DE9801308W WO9906702A1 WO 1999006702 A1 WO1999006702 A1 WO 1999006702A1 DE 9801308 W DE9801308 W DE 9801308W WO 9906702 A1 WO9906702 A1 WO 9906702A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
seal
piston pump
ring
pump
Prior art date
Application number
PCT/DE1998/001308
Other languages
German (de)
English (en)
Inventor
Heinz Siegel
Norbert Alaze
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
Priority claimed from DE19753083A external-priority patent/DE19753083A1/de
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to EP98933502A priority Critical patent/EP0932764A1/fr
Priority to JP11510337A priority patent/JP2001501274A/ja
Publication of WO1999006702A1 publication Critical patent/WO1999006702A1/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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • 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
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
    • B60T13/16—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid using pumps directly, i.e. without interposition of accumulators or reservoirs
    • B60T13/168—Arrangements for pressure supply
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4031—Pump units characterised by their construction or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—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
    • 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
    • F04B1/0421—Cylinders
    • 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
    • F04B53/126—Ball 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
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/143—Sealing provided on the piston
    • 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
    • F04B53/148—Pistons, piston-rods or piston-rod connections the piston being provided with channels which are coacting with the cylinder and are used as a distribution member for another piston-cylinder unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the invention is based on a piston pump according to the type of the main claim, which is intended in particular for use in a hydraulic vehicle brake system with a slip control device.
  • Piston pumps of this type are known per se. They have a piston which is received in an axially displaceable manner in a cylinder bore in a pump housing.
  • a liner can be inserted into the pump housing or the piston can be accommodated directly in the pump housing.
  • the piston can be driven to perform a reciprocating stroke movement in the axial direction.
  • a sealing ring made of soft, rubber-like plastic, often an O-ring, is used for sealing between the piston and the cylinder bore in a piston groove or in a cylinder bore groove. The circumference of the piston can be guided directly in the cylinder bore.
  • the guide ring which, together with the sealing ring, is inserted into the piston groove or into the cylinder bore groove.
  • the guide ring which usually consists of a dimensionally stable plastic, has the advantage that it reduces friction and wear of the piston and the cylinder bore wall.
  • Another advantage of a guide ring is that the piston and / or Cylinder bore with a larger diameter tolerance and lower surface quality can be produced.
  • seals made of a material with sufficient elasticity of their own can only bridge very small gaps at elevated pressures, overall very tight dimensional and shape tolerances must be observed, which means that the effort to manufacture the piston pump is quite high. Often, a support ring is also required to ensure that the seal is not squeezed into the gap. The support ring also increases the manufacturing costs considerably.
  • Piston pumps have the disadvantage that in addition to the sealing ring, an additional support ring and / or an additional plastic guide ring is required. Piston pumps without the guide ring have the disadvantage of greater piston friction, greater wear, tighter manufacturing tolerances of piston and cylinder bore diameters and a necessary, higher surface quality of the piston peripheral surface and the cylinder bore surface, which usually requires grinding or flaring of these surfaces.
  • the piston pump according to the invention with the features of claim 1 has the advantage that because of the spring element biasing the seal against the sliding surface for the seal, a relatively stiff, little inherent elasticity, but particularly low friction and low wear material can be used.
  • a very stiff and relatively inelastic material can be selected for the seal gives the advantage that even relatively large gaps can be permitted even at high pressures.
  • relatively coarse dimensional and shape tolerances can be permitted even without the use of a separate support ring, which advantageously reduces the manufacturing outlay considerably.
  • the advantage of an improvement in the delivery rate and extension of the service life of the piston pump according to the invention is achieved without the need for a separate guide ring.
  • the seal is elastically biased in the radial direction against a sliding surface by the spring element.
  • the seal is elastically expanded in the radial direction by the spring element and thereby pressed in sealing contact against a cylinder bore wall if the seal is axially immovable on the piston and axially displaceable together with the piston in the cylinder bore, or the seal is removed from the
  • the spring element is compressed radially elastically, so that the seal lies sealingly on a piston circumferential surface when it is axially immovably mounted in the cylinder bore and the piston moves axially relative to the seal during its stroke movement.
  • a relatively soft, rubber-like plastic as is usually used for sealing rings, is not suitable as a guide ring.
  • a relatively rigid plastic is in itself not suitable for sealing, since it does not guarantee adequate sealing due to a lack of elasticity or insufficient elasticity, at least in the long run.
  • a guide ring made of rigid plastic loses its sealing effect at the latest at a higher temperature or when there is a change in temperature. This problem is overcome with the aid of the spring element used according to the invention.
  • the spring element ensures that the seal is sufficiently resiliently biased against the sliding surface under all operating conditions. This gives the advantage of good tightness under all operating conditions, even when the hydraulic pressure is low and also when the seal is made of a relatively rigid material.
  • the piston pump is advantageously also suitable for very different operating conditions; at low hydraulic pressure, the spring element ensures sufficient Preloading the seal against the sliding surface and for high hydraulic pressure, the material of the seal can be chosen to be sufficiently rigid.
  • piston return spring which is provided in a high-pressure working chamber of the piston pump and acts in the axial direction, presses the piston of the piston pump into constant contact against an eccentric. This acting in the axial direction piston return spring can be the task of
  • the pressure in the high pressure working space of the piston pump is usually the highest, and when the piston is fully extended, the pressure in the high pressure working space is usually the lowest.
  • the force of the piston return spring is slightly greater than when the piston is extended. Because the force generated by the piston return spring is greatest when the pressure in the high-pressure working space is also greatest, the advantage of a good sealing effect is obtained even at high pressure and less wear at low pressure.
  • the seal has an expansion surface inclined to a radial direction, for example a conical ring surface, which is acted upon directly or indirectly by a force acting in the axial direction by a spring element, that is to say, for example, a helical compression spring. Due to the radially outward or inward inclination of the expansion surface, the axial force of the spring element is converted into a radial force which expands or compresses the seal radially and thereby holds it in sealing contact with the sliding surface, i.e. depending on the design on the cylinder bore wall or the piston circumference 4).
  • a spring element that is to say, for example, a helical compression spring. Due to the radially outward or inward inclination of the expansion surface, the axial force of the spring element is converted into a radial force which expands or compresses the seal radially and thereby holds it in sealing contact with the sliding surface, i.e. depending on the design on the cylinder bore wall or the piston circumference 4).
  • the inclination of the expansion surface which can change in the radial direction of the expansion surface, determines the ratio in which the axial force of the spring element is converted into a radial force sealing the seal against the sliding surface, so that the choice of the inclination of the expansion surface increases the the radial force exerted on the seal can be influenced in a targeted manner.
  • the piston pump 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 to a wheel brake cylinder or to several wheel brake cylinders (ASR or FDR or EHB) .
  • the pump is required, for example, in a brake system with a 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 (ABS or ASR) 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, in order, for example, to prevent the vehicle from breaking out of the lane desired by the driver.
  • the pump can also be used with an Hydraulic brake system (EMS) are used in which the pump delivers the brake fluid into the wheel brake cylinder or in the wheel brake cylinder when an electric brake pedal sensor detects an actuation of the brake pedal or in which the pump serves to fill a memory of the brake system.
  • EMS Hydraulic brake system
  • the piston pump according to the invention shown in FIG. 1, generally designated 10, has a liner 12 which is inserted into a stepped pump bore 14 of a hydraulic block, which forms a pump housing 16.
  • the hydraulic block of which only a fragment surrounding piston pump 10 is shown in the drawing, is part of a slip-controlled hydraulic vehicle brake system, which is otherwise not shown.
  • further hydraulic components such as solenoid valves and hydraulic accumulators are used in it and a master brake cylinder and wheel brake cylinder are connected.
  • the hydraulic components are hydraulically interconnected by means of the hydraulic block.
  • a pin-shaped piston 20 is received in the liner 12 and protrudes a short distance from the liner 12 on one side.
  • the end of the piston 20 protruding from the liner 12 is axially displaceably guided in the pump bore 14 in the pump housing 16 by means of a guide ring 22 and sealed with an O-ring 24 in the pump housing 16.
  • the piston 20 is provided with an axial blind bore 26 from its end located in the liner 12, which is crossed by transverse bores 28 near its base approximately in the longitudinal center of the piston 20.
  • a nominal diameter of the piston 20 corresponds to an inner diameter of the liner 12, with a clearance fit between the piston 20 and the liner 12, ie the piston 20 has an undersize in relation to the liner 12 on, which ensures the axial displacement of the piston 20.
  • the undersize of the piston 20 creates a circumferential gap between the piston 20 and the bushing 12. So that the bushing 12 does not touch even with unfavorable dimensional and shape tolerances of the piston 20, the gap must be of a sufficiently large size.
  • the blind bore 26 and transverse bores 28 communicate through a wide groove 30 in the circumference of the piston 20 and radial bores 32 in the liner 12 with an inlet bore 34 which is radially attached to the piston pump in the pump housing 16 and opens into the pump bore 14 into which the liner 12 is inserted is.
  • the piston pump 10 As the inlet valve 36, the piston pump 10 according to the invention has a spring-loaded check valve which is attached to the end of the piston 20 located in the liner 12.
  • An opening of the blind bore 26 is designed as a conical valve seat 38, against which a valve ball 40 as a valve closing body by a helical compression spring
  • Valve closing spring 42 is pressed.
  • the valve closing spring 42 is supported against a bottom of a cup-shaped valve cage 44, which is made of sheet metal as a deep-drawn part and has passages 46.
  • the valve cage 44 On its open side, the valve cage 44 has a circumferential ring step 48, with which it rests on the end face of the piston 20 located in the liner 12.
  • An inwardly formed, free edge 50 of the valve cage 44 engages in the manner of a clip connection in a groove pierced into the piston 20, as a result of which the valve cage 44 is fastened to the piston 20.
  • Valve ball 40 and valve closing spring 42 are received in valve cage 44.
  • the piston pump 10 To drive the piston 20 to a reciprocating movement in the axial direction, the piston pump 10 according to the invention has an eccentric 52 which can be driven by an electric motor, against the circumference of which the piston 20 is pressed by a piston return spring 54 which is designed as a helical compression spring and in the bushing 12 is arranged and is supported on the liner bottom 18.
  • a cylindrical closure element 56 is placed on the liner bottom 18 and connected to the liner 12 with a flange 58.
  • the caulking element 59 closes the closure element 56 by caulking 59 of the pump housing 16 the pump bore 14 is pressure-tight and fixes the liner 12 in the pump housing 16.
  • An outlet valve 60 in the form of a spring-loaded check valve is accommodated in the closure element 56:
  • the closure element 56 has a coaxial blind bore 62 into which a helical compression spring as a valve closing spring 64 and a valve ball 66 as a valve closing spring are used.
  • the valve ball 66 interacts with a conical valve seat 68, which is attached to an opening of a central bore 70, which axially penetrates the bushing base 18.
  • the valve seat 68 is shaped and solidified by stamping.
  • the fluid is discharged through radial channels 72 between the liner bottom 18 and the closure element 56 into an outlet bore 74 in the pump housing 16.
  • the free volume in the area of the groove 30 and the radial bore 32 serves as a low-pressure chamber 75 of the piston pump 10.
  • a high-pressure working chamber 77 of the piston pump 10 Enlarged or reduced in accordance with the extension and retraction movements of the piston 20 the volume of the high-pressure working space 77.
  • the piston 20 has an annular, circumferential seal 76 which is placed on the end of the piston 20 located in the bushing 12 at an annular step 78, at which the piston 20 tapers towards its end located in the bushing 12.
  • the seal 76 consists of a relatively rigid plastic, for example of PTFE (polytetrafluoroethylene), which has a low coefficient of friction.
  • the seal 76 also serves to guide the piston 20 in the liner 12. In the selected embodiment, the seal can
  • seal 76 are therefore also referred to as sealing and guide rings. Because the seal 76 can be made from a relatively rigid, dimensionally stable plastic, it can also bridge a relatively large gap between the piston 20 and the liner 12. This ensures good tightness and durability, even at high pressures. To turn on at high pressures
  • the seal 76 shown by way of example has an almost rectangular ring cross section, an end face facing the bushing base 18 being conical as an expanding surface 80, or more precisely forming an inner cone, ie imaginary straight lines perpendicular to the expanding surface 80 run obliquely inwards.
  • the piston return spring 54 presses a ring 82 inserted between it and the seal 76 in the axial direction against the seal 76 and via the ring step 78 of the piston 20 the piston 20 in contact with the circumference of the eccentric 52.
  • the ring 82 serves as an expansion ring.
  • the ring 82 is designed as a conical perforated disk with the same cone angle as the spreading surface 80.
  • An end face of the ring 82 which bears against the spreading surface 80 of the seal 76 forms a counter surface 84 to the spreading surface 80.
  • the piston return spring 54 presses the seal 76 radially via the ring 82 with the conical counter surface 84 which bears against the conical spreading surface 80 of the seal 76 apart in sealing contact with the liner 12.
  • the inner circumference of the liner 12 serves as a sliding surface 85. During the stroke movements of the piston 20, the seal 76 slides on the sliding surface 85.
  • An angle of inclination of the counter surface 84 and the expanding surface 80 to a radial direction determines the pressing force of the seal 76 on the bushing 12 in relation to the spring force of the piston return spring 54.
  • the stiffness of the seal 76 is also determined, this stiffness depending on the material stiffness and the cross-sectional area of the seal 76 depends on the Kr aft, with which the seal 76 is pressed against the sliding surface 85. In order to use a sufficiently large, low-wear material for the seal 76 that presses the seal 76 against the sliding surface 85 even when using a stiff, low-wear material
  • the spreading surface 80 can be correspondingly more inclined with respect to the radial direction.
  • the piston return spring 54 at the same time forms a spring element which expands the seal 76 radially and thereby ensures the seal towards the " liner 12.
  • the seal 76 seals off the piston 20 by contacting the ring step 78 of the piston 20.
  • the counter surface 84 and the expansion surface 80 do not have to have the same inclination to the radial direction, in particular the counter surface and / or expansion surface can also be spherical or hollow, for example.
  • the ring 82 serving as an expanding ring can, for example, also have a circular or semicircular ring cross section find use (not shown).
  • the piston return spring 54 can also press directly against the expansion surface 80 of the seal 76 without the interposition of a ring.
  • the same seal 76 as in the piston pump 10 shown in FIG. 1 is used.
  • the conical expansion surface 80 of the seal 76 faces the annular step 78 of the piston 20, which is conical as a counter surface 88 for the expansion surface 80.
  • the piston return spring 54 presses the annular circumferential seal 76 against the inclined counter surface 88, as a result of which the seal 76 is pressed radially apart from one another in sealing contact against the sliding surface 85 provided on the bushing 12.
  • the ring 82 ensures that the seal 76 is not damaged by the piston return spring 54. Because a fairly rigid material can be used for the seal 76, the ring 82 can optionally also be dispensed with without the direct contact of the piston return spring 54 with the seal 76 causing damage to the seal 76.
  • piston pump 10 shown in FIG. 2 corresponds to the piston pump 10 shown in FIG. 1.
  • the same components are provided with the same reference numbers.
  • the end face of the seal 76 facing the ring 82 or the piston return spring 54 is inclined conically with respect to the radial direction.
  • that end of the seal 76 which faces away from the piston return spring 54, together with the ring step 78 of the piston 20, is conically inclined with respect to the radial direction.
  • the piston pump 10 can also be modified such that both the end face of the seal 76 facing the ring 82 or the piston return spring 54 and the end face of the seal 76 facing the ring step 78 are conically inclined. In this case, the direction of inclination of the end face facing the ring 82 or the piston return spring 54 runs as shown in FIG.
  • the piston 20 consists essentially of metal, and the seal 76, which can also serve as a guide for the piston 20 in the bushing 12 or directly in the pump housing 16, is a separate component on the Piston 20 attached.
  • the piston 20 it is also possible to produce the piston 20 partially or entirely from plastic, and it is also possible to form the seal 76 in one piece on the piston 20 or on the part of the piston 20 made of plastic.
  • FIG. 3 shows an embodiment in which the piston 20 essentially consists of a first piston part 20a and a second piston part 20b. Any sealing compound (not shown) applied between the two piston parts 20a, 20b ensures a good seal between these two parts.
  • the first piston part 20a facing the eccentric 52 is made of metal
  • the second pump part 20b accommodated in the liner 12 is made of plastic, preferably of a rigid, dimensionally stable plastic.
  • the seal 76 is integrally formed on the piston part 20b of the piston 20.
  • the end face of the seal 76 facing the piston return spring 54 or the ring 82 is inclined conically or conically.
  • the spreading surface 80 is located on this end face. As FIG. 3 shows, the inclination of the surface of the ring 82 lying against the spreading surface 80 of the seal 76 is adapted to the inclination of the spreading surface 80.
  • the piston return spring 54 acts on the piston 20 in the axial direction, the force of the piston return spring 54 acting in the axial direction on the piston 20 due to the inclination of the expansion surface e 80 causing a force component acting on the seal 76 in the radial direction outward.
  • the piston part 20b essentially only presses the area which is directly acted upon by the piston return spring 54 in the radial direction outward against the sliding surface 85, so that this area of the piston 20 performs the function of the seal 76 in an outstanding manner takes over, even if the piston 20 or the piston part 20b consists of a fairly stiff material with little inherent elasticity.
  • the end of the piston 20 protruding from the liner 12 can be made in the same way with a plastic seal, not shown, which is held by a spring element in sealing contact with the sliding surface instead of with a separate sealing ring 24 and the guide ring 22 must be sealed and guided, like the end of the piston 20 (not shown) located in the liner 12.
  • This embodiment variant, not shown, has a seal that is permanently assigned to the pump housing 16 and is acted upon by the spring element in the radial direction against the sliding surface provided on an outer circumference of the piston.

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

Abstract

L'invention concerne une pompe à piston (10) pour un système de freinage hydraulique de véhicule à antipatinage. L'invention vise à assurer l'étanchéité et le guidage d'un piston (20) de la pompe (10) dans une garniture (12). A cet effet, il est prévu un élément d'étanchéité (76) en matière plastique rigide, présentant une surface d'écartement (80) en forme de cône intérieur, contre laquelle appuie un ressort de rappel de piston (54) directement ou par l'intermédiaire d'un anneau d'écartement (82) présentant une surface correspondante conique (84). L'élément d'étanchéité (76) est ainsi plaqué de façon étanche contre la garniture (12). L'avantage de l'invention réside dans le fait qu'il est pas nécessaire d'avoir recours à un anneau de guidage et d'étanchéité séparé, ce qui permet de réduire le frottement et l'usure.
PCT/DE1998/001308 1997-07-30 1998-05-12 Pompe a piston WO1999006702A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP98933502A EP0932764A1 (fr) 1997-07-30 1998-05-12 Pompe a piston
JP11510337A JP2001501274A (ja) 1997-07-30 1998-05-12 ピストンポンプ

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19732811.3 1997-07-30
DE19732811 1997-07-30
DE19753083A DE19753083A1 (de) 1997-07-30 1997-11-29 Kolbenpumpe
DE19753083.4 1997-11-29

Publications (1)

Publication Number Publication Date
WO1999006702A1 true WO1999006702A1 (fr) 1999-02-11

Family

ID=26038687

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1998/001308 WO1999006702A1 (fr) 1997-07-30 1998-05-12 Pompe a piston

Country Status (4)

Country Link
US (1) US20010048884A1 (fr)
EP (1) EP0932764A1 (fr)
JP (1) JP2001501274A (fr)
WO (1) WO1999006702A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002064976A1 (fr) * 2001-02-12 2002-08-22 Robert Bosch Gmbh Pompe a piston
JP2003500610A (ja) * 1999-05-29 2003-01-07 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
KR100413391B1 (ko) * 2000-07-22 2003-12-31 주식회사 만도 차량용 제동장치의 펌프
WO2004037624A1 (fr) * 2002-10-26 2004-05-06 Continental Teves Ag & Co. Ohg Dispositif de transport
WO2007031472A1 (fr) * 2005-09-14 2007-03-22 Continental Teves Ag & Co. Ohg Pompe a piston
WO2007147693A2 (fr) * 2006-06-22 2007-12-27 Robert Bosch Gmbh Pompe à piston
EP2312155A1 (fr) 2009-10-15 2011-04-20 Delphi Technologies Holding S.à.r.l. Pompe à fluide et piston correspondant

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EP1545952B1 (fr) * 2002-09-24 2008-02-27 Continental Teves AG & Co. oHG Dispositif de refoulement
DE102004037147A1 (de) * 2004-07-30 2006-03-23 Robert Bosch Gmbh Kolbenpumpe mit kompakter Haltevorrichtung für eine Rückstellfeder
DE102005043266A1 (de) * 2004-10-15 2006-04-20 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102005042197A1 (de) * 2005-09-06 2007-03-08 Robert Bosch Gmbh Kolbenpumpe mit verbessertem Kolben
CN100351517C (zh) * 2006-03-07 2007-11-28 大连大学 高压动态相平衡试验用气液输送泵
DE102007018235A1 (de) * 2007-04-18 2008-10-23 Robert Bosch Gmbh Pumpenvorrichtung zur Erzeugung hoher Drücke
JP5034705B2 (ja) * 2007-06-18 2012-09-26 株式会社アドヴィックス ピストンポンプ
DE102009047217A1 (de) * 2009-11-27 2011-06-01 Robert Bosch Gmbh Kolbenplumpe
DE102009047727A1 (de) * 2009-12-09 2011-06-16 Robert Bosch Gmbh Kolbenpumpe mit einem Schließkörper am Einlassventil
JP5505346B2 (ja) * 2011-03-25 2014-05-28 アイシン・エィ・ダブリュ株式会社 電磁ポンプ
JP5867266B2 (ja) * 2012-04-25 2016-02-24 株式会社アドヴィックス ピストン装置
US9174620B2 (en) 2013-01-21 2015-11-03 Kelsey-Hayes Company Slip control braking pump having a high pressure sealing structure
EP3353455B1 (fr) * 2015-09-25 2020-02-12 Bloechlinger Engineering AG Soupape antiretour
KR102600302B1 (ko) * 2018-10-11 2023-11-09 현대모비스 주식회사 브레이크용 피스톤 펌프
CN109236632B (zh) * 2018-11-16 2023-08-15 漯河安润设备有限公司 一种出油可检测的高压柱塞
US11781541B2 (en) * 2021-09-29 2023-10-10 Chipmast Autotronix Co., Ltd. Oil-scavenge pump and method for assembling the same
US11668291B2 (en) * 2021-09-29 2023-06-06 Chipmast Autotronix Co., Ltd. Oil-scavenge pump and method for assembling the same

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EP0421900A1 (fr) * 1989-10-04 1991-04-10 Michel Foa Dispositif d'étanchéité pour organe cylindrique mobile axialement et/ou en rotation dans une chambre
DE4027794A1 (de) * 1990-09-01 1992-03-05 Teves Gmbh Alfred Hydraulische radialkolbenpumpe
JPH0611044A (ja) * 1992-06-22 1994-01-21 Honda Motor Co Ltd パッキン構造体
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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003500610A (ja) * 1999-05-29 2003-01-07 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
JP4828749B2 (ja) * 1999-05-29 2011-11-30 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
KR100413391B1 (ko) * 2000-07-22 2003-12-31 주식회사 만도 차량용 제동장치의 펌프
WO2002064976A1 (fr) * 2001-02-12 2002-08-22 Robert Bosch Gmbh Pompe a piston
WO2004037624A1 (fr) * 2002-10-26 2004-05-06 Continental Teves Ag & Co. Ohg Dispositif de transport
US7478998B2 (en) 2002-10-26 2009-01-20 Continental Teves Ag & Co. Ohg Conveyor device
WO2007031472A1 (fr) * 2005-09-14 2007-03-22 Continental Teves Ag & Co. Ohg Pompe a piston
US8353691B2 (en) 2005-09-14 2013-01-15 Continental Teves Ag & Co., Ohg Piston pump
WO2007147693A2 (fr) * 2006-06-22 2007-12-27 Robert Bosch Gmbh Pompe à piston
WO2007147693A3 (fr) * 2006-06-22 2008-02-28 Bosch Gmbh Robert Pompe à piston
US8272858B2 (en) 2006-06-22 2012-09-25 Robert Bosch Gmbh Piston pump
EP2312155A1 (fr) 2009-10-15 2011-04-20 Delphi Technologies Holding S.à.r.l. Pompe à fluide et piston correspondant

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US20010048884A1 (en) 2001-12-06
EP0932764A1 (fr) 1999-08-04

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