EP2207959A1 - Piston pump - Google Patents
Piston pumpInfo
- Publication number
- EP2207959A1 EP2207959A1 EP08804584A EP08804584A EP2207959A1 EP 2207959 A1 EP2207959 A1 EP 2207959A1 EP 08804584 A EP08804584 A EP 08804584A EP 08804584 A EP08804584 A EP 08804584A EP 2207959 A1 EP2207959 A1 EP 2207959A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- piston pump
- closing body
- pump according
- piston
- 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.)
- Ceased
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
- F04B1/0452—Distribution members, e.g. 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
- 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
- F04B53/1017—Semi-spherical ball valves
Definitions
- the invention relates to a piston pump for a vehicle brake system according to the preamble of claim 1.
- Such piston pumps are used in motor vehicles with hydraulic vehicle brake systems and often referred to as return pumps. With slip control, they serve to selectively lower or increase the brake pressure in the wheel brake cylinders in order to be able to regulate the brake pressure in the wheel brake cylinders.
- the invention has for its object to provide a noise-optimized piston pump for a hydraulic vehicle brake system.
- the invention is based on the idea of minimizing the noise emission of the piston pump by virtue of the fact that the valve closing body of at least one valve of the piston pump has a shaft section and a calotte section which sealingly engages the valve seat of the valve in a closed position of the valve.
- a ball segment section is understood, which has a curved (dome-shaped) surface portion. This preferably cooperates with a valve seat formed in particular as an internal cone seat in such a way that an annular sealing surface or sealing line is obtained when the valve-closing body is in contact with the valve seat.
- a piston pump with a valve closing body designed in this way has a multiplicity of advantages over known piston pumps, in particular with regard to their noise development.
- the vibration behavior of the valve closing body due to the provision of the particular serving as a guide shaft portion over known spherical valve closing bodies can be significantly reduced.
- the shaft section can serve as a stroke limitation, so that the adjustment path of the valve closing body is the same for each opening movement. Due to the spherical segment-shaped (dome-shaped) training of cooperating with the valve seat (front) portion of the valve closing body, the overall construction of the piston pump does not need to be changed, but the optimized in terms of noise valve closing body is used with previously used, inner cone-shaped valve seats.
- valve closing body with a Kalottenabrate and an adjoining shank portion also, especially in a one-piece design of the valve closing body made of plastic, the wear behavior can be optimized at the valve seat, whereby an improved tightness of the valve over the life of the piston pump is obtained.
- piston pump can be used both as a pressure and as a suction pump.
- the valve with optimized valve closing body is the outlet valve of the piston pump.
- the outlet valve When the outlet valve is open, that is, when the valve closing body is lifted off the valve seat, brake fluid flows in the axial direction past the calotte section, preferably to a radial groove embossed in a closure cover, through which the brake fluid can flow out of the piston pump.
- valve closing body is made of steel, or made of plastic as usual, whereby the mass of the valve closing body can be reduced by about a factor of 10 compared to a steel ball.
- the opening pulse of, in particular, as an outlet Valve trained valve reduced, which in turn prevents overshooting of the valve closing body.
- this can further reduce the noise of the piston pump.
- the wear behavior on the valve seat improves.
- a cost-effective and only slightly tolerant production of the valve closing body by injection molding or steel forming part is possible.
- valve closing body made of plastic in one embodiment of the piston pump, in which the shaft portion serves as a guide portion for the valve closing body.
- shaft portion serves as a guide portion for the valve closing body.
- the shaft portion is contoured cylindrical.
- the cylindrical design of the shaft portion allows the integration of the valve closing body in a blind hole with a circular cross section, in particular in a closure cap of the piston pump in a simple manner.
- a plurality of, preferably evenly distributed over the circumference, guide ribs are provided on the shaft portion, with which the shaft portion and thus the entire valve closing body is guided in a blind hole or a receiving hole in the radial direction.
- the guide ribs extend in the axial direction, preferably over at least almost the entire axial extension of the, in particular between adjacent guide ribs cylindrical, shaft portion.
- twice the radius of curvature of the calotte section ie twice the radius of curvature of the curved surface of the front section of the valve-closing body, is greater than the diameter of the shaft section.
- the double radius of curvature of the calotte portion is even greater than the (outer) diameter of the shaft portion of the valve closing body formed by the guide ribs.
- valve seat with which the valve closing body or its calotte section sealingly cooperates, is preferably formed on the bushing, in particular on the end face thereof.
- the space can be further optimized in a piston pump with a valve closing body, which has a Kalottenabêt and a shaft portion, ie exploited, in particular reduced, that the cooperating with the valve closing body closing spring in sections within the shaft portion, in particular radially within an outer guide surface, is received.
- a front-side annular groove extending in the axial direction is preferably provided for receiving the closing spring, wherein the annular groove is preferably arranged at a radial distance from the lateral surface or from the guide ribs of the shaft section.
- a stroke stop for axially limiting the stroke movement of the valve closing body is formed by a core section of the valve closing body enclosed by the closing spring. Additionally or alternatively, the stroke stop can be formed by an end face of a peripheral wall section.
- the Kalottenabrough or the curved surface portion is formed as a ring portion, the Kalottenabrough frontally of a flattened, in particular circular surface portion is limited.
- 1 shows a detail of a piston pump with an optimized outlet valve
- 2a is a perspective view of an optimized valve closing body obliquely from the front
- FIG. 2b shows a longitudinal sectional view of the valve closing body according to FIG. 2a, FIG.
- FIG. 3a shows a perspective view of a valve closing body with four equally distributed over the circumference guide ribs and
- FIG. 3b a longitudinal sectional view of the valve closing body of FIG. 3a.
- a piston pump 1 is shown. This is arranged in a hydraulic block 2, in which, apart from the piston pump 1, further components, not shown, of a hydraulic vehicle brake system having a slip control, such as solenoid valves, check valves and hydraulic accumulators, are housed and hydraulically interconnected.
- the hydraulic block 2 forms a pump housing of the piston pump 1.
- a multi-stepped pump bore 3 is arranged.
- the piston pump 1 has a pump piston 4, one of which, a displacement chamber 5 opposite end with a ring seal 6 (low pressure seal) against a Eccentric 7 is sealed.
- an eccentric 8 is rotatably driven about a perpendicular to the longitudinal extent of the pump piston 4 extending axis of rotation rotatably, the pump piston 4 facing away from the displacer 5 end face 9 rests on the circumference of the eccentric 8, which drives the pump piston in the axial direction.
- the displacer 5 facing the end of the pump piston 4 is received in a bushing 10 (pump cylinder), which sits in the pump bore 3 by means of a press fit.
- the interference fit provides a seal between the inlet and outlet sides, i.
- Axially on the pump piston 4 includes in the direction of the displacement chamber 5, a plastic sealing element 38 which rests radially outwardly on the inner circumference of the bushing 10, and which seals the displacement chamber 5 in the direction of a pump inlet of the piston pump 1 ,
- an axial passage 11 which continues in the pump piston 4 is provided in the plastic sealing element 38 and is crossed near its base by transverse bores 12.
- the axial channel which is designed as a blind hole in the pump piston 4, and the transverse bores 12 communicate with an inflow bore 13 in the hydraulic block 2.
- a check valve is provided as the inlet valve 14.
- the inlet valve 14 has a valve plate 15 (alternatively eg valve ball) which cooperates with a conical inlet valve seat 16, which at an orifice of the axial channel 11 is attached to the plastic sealing element 38.
- a helical compression spring as inlet valve closing spring 17 presses the valve ball 15 against the inlet valve seat 16.
- the valve ball 15 and the inlet valve closing spring 17 are received in an inlet valve housing 18, which is formed as a cup-shaped injection molded part made of plastic with flow openings, not shown.
- the inlet valve housing 18 has an annular step 19 on which a return spring 20 for the pump piston 4, which is arranged within the displacement chamber 5, engages. In the axial direction, the inlet valve housing 18 is supported on the plastic sealing element 38, which is thereby subjected to force against the pump piston 4.
- the piston pump 1 has a valve 21 designed as an outlet valve. This is how the inlet valve 16 is formed as a check valve.
- a blind hole 23 (outlet valve chamber) is arranged centrally.
- a closing spring 24 (helical compression spring) of the valve 21 is arranged.
- the closing spring 24 is supported at one end at the bottom of the blind hole 23 and at the other end against a valve closing body 25 of the valve 21.
- the designed as an injection molded plastic valve closing body 25 has a right in the plane of the drawing, the Verdrängerraum 5 facing Kalottenab mustard 26 and an adjoining in the axial direction, in the direction of the bottom of the blind hole 23 extending shank portion 27.
- the valve closing body 25 is guided on the circumference of the blind hole 23.
- the trained as a circumferential ring, part spherical surface 28 (dome) of the Kalottenabterrorismes 26 cooperates with an inner cone-shaped valve seat 29 which is formed on the left in the drawing plane end face of the bush 10.
- hydraulic fluid (brake fluid) located in the displacement chamber 5 can flow axially between the dome section 26 and the valve seat 29 into the blind hole 23 and from there via a radial groove 30 impressed into the closure cover 22 to an outflow channel 31.
- the lifting movement of the valve closing body 25 is limited by a stroke stop 32 (stroke limitation), which is formed by the located in the left half of the drawing end side of the shank portion 27, more precisely from the end face of a central portion 33 of the valve closing body 25. Due to the provision of the shaft portion 27, which is guided with its outer circumference on the inner circumference of the blind hole 23, vibrations of the valve closing body 25 are minimized during its adjustment movement. In addition, the opening pulse is minimized due to the integral formation of the valve closing body 25 made of plastic.
- the double radius R of the curved surface 28 is greater than the diameter D of the cylindrical shaft portion (2R> D), whereby a large opening cross-section of the valve 21 is realized. This results in a rapid outflow of Hydraulic fluid from the displacement chamber 5 and as a result a rapid pressure change in the brake cylinder (not shown).
- the closing spring 24 extends in the axial direction into an end-side annular groove 34 in the valve closing body 25.
- the annular groove 34 encloses the central portion 33, the free end face forms the stroke stop.
- the axial extent of the annular groove is about 2/3 of the axial extent of the shaft portion 27th
- a possible embodiment of the valve closing body 25 is shown.
- the (pre-) Kalottenabrough 26 with its partially curved surface 28.
- the curved surface 28 extends annularly around the Kalottenabrough 26, the end face 35 is formed flattened. In this case, the circular end face 35 extends perpendicularly to the longitudinal extent of the valve closing body 25.
- the cylindrical shaft section 27 adjoins the dome section 26 in the axial direction.
- the diameter D (see Fig. 2b) of the shaft portion 27 corresponds to the diameter of the blind hole 23 minus a minimum guide clearance.
- the radius of curvature R of the curved surface 28 of the calotte section 26 is greater than half the diameter of the shaft section 27.
- Ring groove 34 serves, as can be seen from FIG. sectional recording of the trained as a helical compression spring closing spring 24 of the valve 21st
- FIG. 3b an alternative embodiment of a valve closing body 25 made of plastic (alternatively Stahlumformteil) is shown.
- the cylindrical shaft portion 27 is provided with four equally circumferentially spaced guide ribs 37, which extend almost over the entire longitudinal extent of the shaft portion 27 and which serve to guide the valve closing body 25 on the inner periphery of the blind hole.
- the guide ribs 37 By providing the guide ribs 37, the outflow behavior (larger outflow cross-section) of the hydraulic fluid can be improved.
- the radius of curvature R of the calotte section 6 is more than twice as large as half the diameter D of the shaft section, the diameter D of the shaft section being formed by the guide ribs 37 in the embodiment shown. is limited. Otherwise, the embodiment of the valve closing body 25 according to FIGS. 3a and 3b corresponds to the exemplary embodiment shown in FIGS. 2a and 2b.
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)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200710052755 DE102007052755A1 (en) | 2007-11-06 | 2007-11-06 | piston pump |
PCT/EP2008/062664 WO2009059842A1 (en) | 2007-11-06 | 2008-09-23 | Piston pump |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2207959A1 true EP2207959A1 (en) | 2010-07-21 |
Family
ID=40160024
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08804584A Ceased EP2207959A1 (en) | 2007-11-06 | 2008-09-23 | Piston pump |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2207959A1 (en) |
DE (1) | DE102007052755A1 (en) |
WO (1) | WO2009059842A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010040193B4 (en) | 2010-09-03 | 2021-07-22 | Robert Bosch Gmbh | Piston pump with a discharge |
DE102017216900A1 (en) * | 2017-09-25 | 2019-03-28 | Robert Bosch Gmbh | Pressure medium control valve, in particular for controlling a flow direction in a pressure medium circuit and piston pump, in particular for the promotion of a pressure medium in an electronically slip-regulated vehicle brake system |
EP4382746A2 (en) | 2020-11-27 | 2024-06-12 | Erbe Elektromedizin GmbH | Pump unit for medical purposes |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19648408A1 (en) | 1996-11-22 | 1998-05-28 | Bosch Gmbh Robert | Piston pump for supplying anti-lock braking system for vehicles |
DE19732770A1 (en) | 1997-07-30 | 1999-02-04 | Bosch Gmbh Robert | Piston pump |
-
2007
- 2007-11-06 DE DE200710052755 patent/DE102007052755A1/en not_active Withdrawn
-
2008
- 2008-09-23 EP EP08804584A patent/EP2207959A1/en not_active Ceased
- 2008-09-23 WO PCT/EP2008/062664 patent/WO2009059842A1/en active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2009059842A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2009059842A1 (en) | 2009-05-14 |
DE102007052755A1 (en) | 2009-05-07 |
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Legal Events
Date | Code | Title | Description |
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PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
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17P | Request for examination filed |
Effective date: 20100607 |
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AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR |
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AX | Request for extension of the european patent |
Extension state: AL BA MK RS |
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17Q | First examination report despatched |
Effective date: 20101025 |
|
R17C | First examination report despatched (corrected) |
Effective date: 20101110 |
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DAX | Request for extension of the european patent (deleted) | ||
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R003 |
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STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION HAS BEEN REFUSED |
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18R | Application refused |
Effective date: 20170114 |