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
  • 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
• • 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
  • F04B1/0452—Distribution members, e.g. 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
  • F04B53/1002—Ball valves
  • F04B53/1007—Ball valves having means for guiding the closure member
• • 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
• • 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

• Piston pump for conveying a fluid and associated brake system
• the invention relates to a piston pump for conveying a fluid according to the preamble of independent claim 1, which is used in particular in brake systems of vehicles.
• Such piston pumps are preferably used in vehicles with hydraulic or electrohydraulic vehicle brake systems as reclaim pumps to selectively lower or increase a brake pressure in the wheel brake cylinders, whereby the brake pressure in the wheel brake cylinders can be regulated.
• a control can be performed, for example, in an antilock brake system (ABS), in a traction control system (ASR system), in a vehicle dynamics control system, and so on.
• Figs. 1 to 3 show a conventional piston pump used in a vehicle brake system.
• a conventional piston pump 1 comprises a piston assembly 2, which has a first piston element 2.1 with a sealing element 13 and a second piston element 2.2, an inlet valve 5, an outlet valve 6 and a cylinder 8.
• the inlet valve 5 is formed as a check valve and comprises a cage member 11, in which an inlet valve spring 5.2 and an inlet valve sealing element 5.3 is arranged, wherein the inlet sealing element 5.3 is designed for example as a sealing disc, which can sealingly cooperate with a corresponding inlet valve seat 5.1, the second piston element 2.2 is arranged, wherein the second piston element 2.2 is non-positively connected to the cage member 11.
• the outlet valve 6 is likewise designed as a spring-loaded check valve and arranged in a cover element 12.
• the outlet valve 6 is opened when a pressure in a compression chamber 8 is greater than a spring force of an outlet valve spring 6.3 acting on an outlet valve sealing element 6.2 of the outlet valve 6, as a result of which Lassventildelement 6.2 is pressed from a arranged on an outlet 8.3 of the cylinder 8 exhaust valve seat 6.1.
• a restoring force F2 arranged in the compression chamber 8.1 and guided by a cylinder wall 8.4 return spring 10 for example is designed as a spiral spring with ground end turns and is supported on a cylinder base 8.2 and on a cage element 11, acts against the cage element 11 of the inlet valve 5 and thus against the second piston element 2.2, around the piston assembly
• a return spring is designed as a simple cylindrical coil spring, that is executed without ground end turns.
• the return spring designed as a spiral spring is supported axially with an upper end winding on a cage element and with a lower end turn on a cylinder bottom, wherein the cage element has an elastic high-pressure sealing element, which towards a cylinder wall a radial bearing area for receiving and centering the upper end turn.
• the return spring has, and wherein the cylinder, in which the return spring is arranged, at a transition between the cylinder wall and the Zylin- derêt for guiding the return spring has an adapted to the under end winding cylinder bottom radius.
• the return spring designed as a spiral spring can be produced inexpensively.
• the notch stress can be reduced by the cylinder bottom radius, as a result of which the cylinder bottom can be made extremely thin so that the component length can be reduced in an advantageous manner.
• the cylinder bottom radius corresponds for example to a radius of the spring wire of the return spring.
• the radial contact area for the upper end of the coil designed as a spiral spring return spring is designed as a radial receiving groove, whereby the return spring designed as a spiral spring can be performed centered centered without sanding Win- ends.
• the radial receiving groove can be formed on the outer edge as a flexible sealing lip, which closes the compression chamber to the cylinder wall pressure-tight, the sealing lip in the load case can seal pressures up to 100 bar. Due to the combination of the radial receiving groove and the sealing lip, the high-pressure sealing element advantageously builds very short.
• the elastic high-pressure sealing element is designed to receive radially acting force components and seal the compression chamber at higher pressures, eg up to 500 bar, via a radial sealing surface against the cylinder wall, wherein the radial sealing surface is formed by a pressure-induced expansion of the high-pressure sealing element, and - A -
• the high-pressure sealing element seals axially via an axial sealing surface against a piston assembly, which is returned by the return spring via the high-pressure sealing element into an initial position.
• the high-pressure sealing element is supported at higher pressures by the rigid cylinder wall and the rigid valve seat, both of which are made of a wear-resistant material. As a result, the high-pressure sealing element only needs to absorb small differential pressure forces and thus experiences only a slight elongation.
• the piston assembly comprises a first piston element and a second piston element, wherein an inlet valve seat consists of a wear-resistant material and is arranged on the second piston element which receives axially acting force components.
• an inlet valve seat consists of a wear-resistant material and is arranged on the second piston element which receives axially acting force components.
• the elastic high-pressure sealing element axially seals against the second piston element via the axial sealing surface. Since the high-pressure sealing element absorbs the radially acting force components, the piston assembly coupled to the high-pressure sealing element only has to absorb the acting axial forces and undergoes no further deformation due to additional radial forces. This division of the axial and radial force components on each component advantageously leads to a reduction in the
• the piston pump according to the invention allows an extreme Kostenreduzie- rank of Kolbenbaudrappe and easy installation.
• the piston pump according to the invention provides improved wicking performance, higher resistance to galling and an extremely short inlet area.
• the first piston element is designed, for example, as a cylindrical needle roller and is advantageously disposed of. se as a mass-produced standard part available. Since a transmission of the driving force of an eccentric is effected via a line contact on the first piston part designed as a solid metal needle roller, preferably as a steel needle roller, the wear can be reduced in an advantageous manner.
• Fig. 1 shows a schematic perspective view of a conventional piston pump.
• Fig. 2 shows a schematic sectional view of a conventional piston pump.
• FIG. 3 shows a schematic perspective illustration of the components of an emissive valve for the conventional piston pump according to FIG. 1 or 2.
• FIG. 4 shows a schematic perspective view of the components of an emissive valve for a piston pump according to the invention.
• FIG. 5 shows a schematic sectional representation of a compression region of a piston pump according to the invention.
• a piston pump according to the invention which can be used as a return pump in a vehicle brake system, essentially comprises the same components as the conventional piston pump 1 described with reference to FIGS. 1 to 3. Therefore, to avoid text repetition, only the essential differences between the piston pump according to the invention and the conventional piston pump 1 according to FIGS. 1 to 3 described in detail. Unlike the conventional Chen piston pump 1 shown in FIG. 1 to 3, the piston pump according to the invention comprises an improved return spring in combination with a high pressure sealing element.
• the inlet valve 25 of the piston pump according to the invention comprises, analogously to the conventional piston pump 1, a cage element 31, in which a
• the piston assembly 22 comprises a first piston element 22.1, which is embodied here by way of example as a cylindrical needle roller, and the second piston element 22.2, wherein the inlet valve seat 25.1 consists of a wear-resistant or of a hard material.
• the cage element 31 of the piston pump according to the invention has an elastic high-pressure sealing element 31.1 designed to accommodate radially acting force components F3 and at pressures up to 100 bar via a radial sealing lip 31.2 and at higher pressures via an additional radial Seal sealing surface 31.3 against a cylinder wall 28.4 shown in FIG. 5 and axially sealed against the piston assembly 22 via an axial sealing surface 31.5, ie against the second piston element 22.2, which rests against the axial sealing surface 31.5.
• the second piston element 22.2 receives only the axially acting force components F1 and F2, so that a longitudinal bore 24 and transverse bores 23 corresponding to the longitudinal bore 24 can be introduced in the second piston element 22.2.
• the cage member 31 are executed with the elastic high-pressure sealing element 31.1 and the second piston member 22.2 with the inlet valve seat 25.1 as plastic injection molded parts, which advantageously allows a simple, inexpensive production of the components, with a complex shape design is possible.
• the first piston element 22.1 in the illustrated embodiment fixed to the second
• Piston element 22.2 coupled.
• the first piston element 22.1 can be loosely coupled to the second piston element 22.2.
• the inventive design of the inlet valve 25 in combination with the piston assembly 22 allows an extreme cost reduction of the piston pump and a simple assembly.
• the piston pump according to the invention provides a Improved suction, a higher pressure resistance and an extremely short Emiass Kunststoff available.
• the piston assembly 22 is longitudinally movably guided with the inlet valve 25 in a cylinder 28 of a compression section 40, wherein fluid is drawn radially through the transverse bores 23 in the second piston element 22.2 during a suction stroke of the piston assembly 22 and radially through the transverse bores 23 corresponding longitudinal bore 24 is guided through the open inlet valve 25 in a compression space 28.1.
• the direction of movement of the piston group 22 reverses, so that the second piston element 22.2 with the inlet valve seat 25.1 is pressed sealingly against the inlet valve sealing element 25.3 via the first piston element 22.1 driven by an eccentric, not shown, and the inlet valve 25 is closed.
• a restoring force F2 of a arranged in the compression space 28.1 return spring 30, which is designed as a simple coil spring without ground loop ends presses against a radial bearing area 31.4, which is arranged on the high-pressure sealing element 31.1.
• the restoring force F2 is axially via the high-pressure sealing element 31.1 and the axial sealing surface 31.5 on the second piston element 22.2, whereby the piston assembly 22 is moved again in the direction of top dead center.
• the radial receiving area 31.4 is designed for receiving and centering an upper end turn 30.1 of the restoring spring, for example, as a radial Aufhahmeut in which runs as a spiral spring return spring 30 is supported with the upper end turn 30.1.
• the combination of the radial Aufhahmenut 31.4 and the sealing lip 31.2 builds the
• High pressure sealing element 31.1 advantageously very short.
• the return spring 30 Via a lower end turn 30.2, the return spring 30 is supported on a cylinder bottom 28.2.
• the cylinder 28 at the transition between the cylinder wall 28.4 and the cylinder bottom 28.2 for guiding the return spring 30 has a cylinder bottom radius 28.4 adapted to the end winding 30.2.
• the cylinder bottom radius 28.4 corresponds to preferred
• the return spring 30 designed as a spiral spring can be produced cost-effectively.
• the notch stress can be reduced by the cylinder bottom radius 28.5, whereby the cylinder bottom 28.2 is made extremely thin and the component length can be advantageously reduced.
• the radial annular groove 31.4 is formed on the outer edge as a flexible sealing lip 31.2, which closes off the compression space 28.1 in a pressure-tight manner against the cylinder wall 28.4. Since the elastic high-pressure sealing element 31.1 between the metallic return spring 30 and that of a wear-resistant and therefore harder
• second piston element 22.2 is arranged, the radial sealing surface 31.3 expanded due to pressure, so that the high pressure sealing element 31.1 sealingly abuts with its full radial outer diameter of the cylinder wall 28.4.
• the high-pressure sealing element 31.1 seals radially against the cylinder wall 28.4 via the radial sealing surface 31.3 and against the second piston element 22.2 through the axial sealing surface 31.5.
• the inlet valve sealing element 25.3 seals axially against the inlet valve seat 25.1 in the first piston element 22.2.
• the component sizes of the high-pressure sealing element and the cylinder are advantageously reduced. Due to the design without ground end turns, the return spring designed as a spiral spring can be produced inexpensively. Overall, the invention allows a cost-effective and space-optimized piston pump with easy-to-manufacture components, which are designed as plastic injection molded parts, the high-pressure sealing element with support by surrounding components up to 500 bar high pressure, the sealing function in the low pressure range below 100 bar through the sealing lip on the high pressure seal is performed.

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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)

Applications Claiming Priority (2)

Publications (1)

Family

ID=40149652

Family Applications (1)

Country Status (5)

Families Citing this family (13)

Family Cites Families (9)

• 2007
  • 2007-10-04 DE DE102007047417A patent/DE102007047417A1/de active Pending
• 2008
  • 2008-09-18 WO PCT/EP2008/062453 patent/WO2009043733A1/de active Application Filing
  • 2008-09-18 CN CN2008801097789A patent/CN101815863B/zh active Active
  • 2008-09-18 EP EP08804391A patent/EP2205866A1/de not_active Withdrawn
  • 2008-09-18 US US12/681,733 patent/US9360008B2/en active Active

Non-Patent Citations (1)

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