EP3194772B1 - Kolbenpumpe - Google Patents

Kolbenpumpe Download PDF

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Publication number
EP3194772B1
EP3194772B1 EP15767111.6A EP15767111A EP3194772B1 EP 3194772 B1 EP3194772 B1 EP 3194772B1 EP 15767111 A EP15767111 A EP 15767111A EP 3194772 B1 EP3194772 B1 EP 3194772B1
Authority
EP
European Patent Office
Prior art keywords
piston
pump
valve
stepped piston
stepped
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.)
Active
Application number
EP15767111.6A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3194772A1 (de
Inventor
Jens Norberg
Patrick Schellnegger
Andreas Lechler
Oliver Gaertner
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 EP3194772A1 publication Critical patent/EP3194772A1/de
Application granted granted Critical
Publication of EP3194772B1 publication Critical patent/EP3194772B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B5/00—Machines or pumps with differential-surface 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
    • F04B1/0408—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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • 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
    • 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
    • F04B9/042—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 cams

Definitions

  • the invention relates to a piston pump with the features of the preamble of claim 1.
  • the piston pump is provided for a slip-controlled hydraulic vehicle brake system.
  • a piston pump according to the features of the preamble of claim 1 is known from EP 0 945 614 A2 already known.
  • a displacement chamber and a step room communicate with a pump outlet such that a stepped piston displaces pressure medium from the displacement chamber during a forward stroke while the step space is blocked from the pump outlet and the stepped piston displaces pressure medium from the step room into the pump outlet on a return stroke while the displacement chamber is shut off from the pump outlet.
  • a piston pump is known in which, during a forward stroke of the stepped piston, a first part of the volume displaced from the displacement chamber flows into the step space and a second part of the displaced volume flows to the pump outlet.
  • the pressure medium flows from the step room to the pump outlet, while the stepped piston is filled with new pressure medium via a pump inlet.
  • the patent application DE 10 2004 061 810 A1 discloses a piston pump with a stepped graduated piston which is axially displaceable in an internally also graduated pump bore.
  • the pump bore does not need to be drilled but can basically be made in any way.
  • the known piston pump on an eccentric, which is arranged on an eccentric end face of the stepped piston and rests on the circumference of the stepped piston with its front end.
  • the stepped piston of the known piston pump On a side facing away from the eccentric, which here refers to the unique designation as displacement side is limited, the stepped piston of the known piston pump a displacement chamber in the pump bore, the volume of the stepped piston alternately reduced in a reciprocating stroke movement and increased.
  • the piston stroke, in which the volume of the displacement chamber decreases, is referred to here as a forward stroke
  • the stroke in the opposite direction, in which the volume of the displacement chamber increases is referred to here as a return stroke.
  • the stepped piston of the known piston pump has an annular space facing away from the displacement chamber, which limits a space in the pump bore, which is referred to here for clarity as step room.
  • a volume change of the step room is inversely increased to the volume change of the displacement chamber, the forward stroke of the stepped piston and the return stroke of the stepped piston, the volume of the step space decreases.
  • the stepped space of the known piston pump is an annular space surrounding the stepped piston in the pump bore, whose cross section is smaller than a cross section of the displacement space, so that the volume change of the step space opposite the displacement space is smaller during the stroke movement of the stepped piston.
  • the step room and the displacement room communicate with a pump outlet.
  • the stepped piston of the known piston pump displaces fluid from the displacement space into the pump outlet and sucks fluid from the pump outlet into the step room. Because the volume change of the displacement space is greater than the volume change of the step room, the piston pump displaces fluid from the pump bore into the pump outlet during the forward stroke.
  • the known piston pump draws fluid from a pump inlet through an inlet valve into the displacement chamber, whose volume increases during the return stroke, and displaces fluid from the step chamber into the pump outlet.
  • the known piston pump thus has the advantage that it displaces fluid into the pump outlet both during a forward stroke and during a return stroke, whereby a fluid volume flow in the pump outlet is more uniform and pressure pulsations are lower.
  • the displacement space and the step room have cross-sectional ratios of 2: 1, so that the piston pump displaces the same amount of fluid into the pump outlet in both strokes.
  • the piston pump according to the invention with the features of claim 1 has a stepped piston with one or more piston stages.
  • the stepped piston is preferably cylindrical with one or more diameter increments, ie ring stages forming one or more piston stages. A cylindrical shape and However, ring stages are not mandatory for the invention.
  • the stepped piston is arranged in a likewise stepped pump bore and driven to a reciprocating stroke movement.
  • the pump bore is an inner surface of a cylinder, a pump housing, a hydraulic block or the like, in which the stepped piston is slidably disposed. It may be manufactured in a manner other than by drilling and, like the stepped piston, is preferably but not necessarily cylindrical and has one or more diameter steps.
  • the stepped piston delimits a displacement space in the pump bore whose volume changes during a stroke movement of the stepped piston depending on its direction of movement.
  • a space in the pump bore which is referred to here as step room.
  • the volume of the step room also changes, but conversely how the volume of the displacement chamber changes. While the volume of the displacement chamber is reduced in the case of a stroke of the stepped piston which is referred to here as an unambiguous designation as a forward stroke, the volume of the step space increases.
  • a cross section of the step room is smaller than a cross section of the displacement space, so that the volume change of the displacement space during a stroke movement of the stepped piston is greater than the inverse volume change of the step room.
  • the cross sections of the displacement space and the step room are in a ratio of 2: 1 to each other.
  • the stepped piston of the piston pump of the present invention displaces fluid from the displacement space into a pump outlet and simultaneously draws a smaller amount of fluid from the pump outlet or the displacement chamber into the step room, such that the piston pump collects fluid into the pump outlet during a forward stroke of its stepped piston repressed.
  • the piston pump sucks in fluid from a pump inlet into the displacement chamber and displaces fluid from the step chamber into the pump outlet, so that the piston pump according to the invention displaces fluid into the pump outlet even during a return stroke.
  • a cross-sectional ratio of 2: 1 the displacement volumes for the forward stroke and the return stroke are the same.
  • the piston pump has a valve through which the step room communicates with the pump outlet.
  • the step chamber can be hydraulically separated from the pump outlet by the valve under certain operating conditions. For example, at high back pressure in the pump outlet, the valve can close and thereby hydraulically separate the step room from the pump outlet, so that the stepped piston displaces at high back pressure in the pump outlet not with the piston stage but only with the displacement side fluid.
  • a pressure-controlled valve is provided as a valve which closes when a pressure in the pump outlet exceeds a closing pressure of the valve or a differential pressure valve is provided which closes when a pressure difference between the pump outlet and the step room exceeds a closing pressure of the differential pressure of the pressure valve.
  • Claim 2 provides a check valve for the step room, which prevents backflow of fluid from the pump outlet into the step room.
  • Claim 3 is directed to that the pump piston is also formed on a suction side as a stepped piston, so that also distributes a Ansaugvolumenstrom the piston pump according to the invention on the forward stroke and the return stroke.
  • This embodiment of the invention has the advantage of a more uniform volume flow and lower pressure pulsations on the suction side of the piston pump.
  • FIG. 1 shows an axial section of a piston pump according to the invention.
  • the drawing is as schematic and simplified To understand illustration for explanation and understanding of the invention.
  • the inventive piston pump 1 is provided as a hydraulic pump for a slip-controlled, hydraulic vehicle brake system, in which such hydraulic pumps are also referred to as return pumps. It serves to build up pressure, increase the pressure and return of brake fluid when lowering wheel brake pressures during or during slip control or braking.
  • the piston pump 1 is arranged in a hydraulic block 2, which can also be understood as a pump housing.
  • the hydraulic block 2 is a block-shaped metal block, for example of an aluminum alloy, in which, apart from the piston pump 1, further hydraulic components of a slip control are arranged and hydraulically interconnected by a bore of the hydraulic block.
  • Such other hydraulic components of a slip control are solenoid valves, check valves, hydraulic accumulator, damper. Hydraulic blocks for slip control are known and will not be discussed further here.
  • the piston pump 1 has a hollow cylindrical bushing 3, which can be considered as a cylinder of the piston pump 1 and in which a diameter-graded cylindrical stepped piston 4 is received axially displaceable.
  • a rotatably driven eccentric 5 is arranged, whose axis of rotation extends radially to an axis of the stepped piston 4.
  • the stepped piston 4 has two conical diameter increments, with which it widens in the direction of the bush bottom 7.
  • the diameter steps are referred to here as piston stages 8, 9.
  • the bushing 3 is inside diameter-matched to the stepped piston 4, the stepped piston 4 is located between the piston stages 8, 9 and with its largest diameter, ie on a side facing away from the eccentric 5 of the eccentric 5 distant and larger piston stage 8 inside cylindrical inner surfaces of the liner 3 on.
  • An inner side of the bushing 3, which, as already mentioned, can also be understood as a cylinder, can be regarded as a pump bore 10, regardless of the manner of its manufacture.
  • the eccentric 5 distant piston stage 8 of the stepped piston 4 is sealed with sealing rings 11 in the pump bore 10.
  • the stepped piston 4 of the piston pump 1 is radially crossed by a bore which forms a pump inlet 12 and a suction side of the piston pump 1.
  • the pump inlet 12 communicates with an annular suction chamber 14 of the piston pump 1, which is formed in the bushing 3 between an eccentric cylinder stage 15 and the eccentric piston stage 9.
  • the stepped piston 4 has an axial blind hole 16, which opens at a the eccentric 5 distant end side of the stepped piston 4, which is referred to here as the displacement side 17.
  • the axial blind hole 16 is crossed by radial bores 18, through which the blind hole 16 communicates with the pumping event 12.
  • a check valve is arranged as the inlet valve 20 of the piston pump 1.
  • the inlet valve 20 has a ball as a shut-off body 21, which is acted upon by a valve spring 22 against the valve seat 19.
  • the shut-off body 21 and the valve spring 22 are received in a cylindrical tubular valve cage 23 which has a flange 24 which is held by the piston spring 6 on the displacement side 17 of the stepped piston 4.
  • the piston pump 1 has a displacement space 25 in the bushing 3, the volume of which alternately decreases and increases in the reciprocating stroke movement of the stepped piston 4.
  • a movement of the stepped piston 4 away from the eccentric 5 is referred to here as a forward stroke, it reduces the Volume of the displacement chamber 25.
  • An opposite movement of the stepped piston 4 in the direction of the eccentric 5 is referred to here as a return stroke and increases the volume of the displacement chamber 25. Due to the increase in volume of the displacement chamber 25 during the return stroke of the stepped piston 4, the piston pump 1 sucks brake fluid from the inlet 12 the intersecting radial bores 18, the axial blind hole 16 and the opening inlet valve 20 in the displacement chamber 25 at.
  • a volume of the suction chamber 14 decreases during the return stroke of the stepped piston 4, the stepped piston 4 displacing brake fluid from the suction chamber 14 through the passages 13 into the pump inlet 12 with the eccentric piston stage 9. This reduces a suction volume during the return stroke of the pump piston 4 through the pump inlet 12. Because a cross-sectional area of the suction space 14 is smaller than a cross-sectional area of the displacement space 25, the volume of brake fluid displaced from the suction space 14 into the pump inlet 12 during the return stroke is smaller than that in FIGS Displacement space 25 sucked brake fluid volume, so that there is still a sucked through the pump inlet 12 brake fluid volume.
  • the cross-sectional areas of the displacement chamber 25 and the suction chamber 14 have a ratio of 2: 1, so that in a return stroke of the stepped piston 4 half as much brake fluid from the suction chamber 14 into the pump inlet 12 displaces as is sucked into the displacement chamber 25.
  • the inlet valve 20 is closed and the volume of the suction chamber 14 increases, so that the piston pump 1 also draws brake fluid through the pump inlet 12 during the forward stroke of the stepped piston 4.
  • the cross-sectional ratio of the displacement chamber 25 and the suction chamber 14 is 2: 1, the flowing brake fluid volumes during a forward stroke and a return stroke of the stepped piston 4 through the pump inlet 12 are equal.
  • the suction and displacement of brake fluid in the suction chamber 14 causes an intake of brake fluid in the manner explained both in the forward stroke and the return stroke and a consequent more uniform intake flow and lower pressure pulsations on the suction side of the piston pump. 1
  • the bush bottom 7 has a center hole 26, the outer mouth of which is a valve seat of an outlet valve 27 of the piston pump 1 forms.
  • the outlet valve 27 is formed in the illustrated and described embodiment, as well as the inlet valve 20 as a check valve and has a ball as shut-off 28, which is acted upon by a valve spring 29 from the outside against the valve seat forming the mouth of the center hole 26 in the bush bottom 7.
  • the shut-off body 28 and the valve spring 29 are arranged in a blind hole 30 in a pump cover 30, which is pressure-tight pressed or caulked in the hydraulic block 2.
  • a radial gap 32 which merges into an annular gap 33 enclosing the bushing 3, into which a radial bore opens which forms a pump outlet 34, which can also be regarded as the pressure side of the piston pump 1.
  • a forward stroke of the stepped piston 4 reduces the volume of the displacement chamber 25 and displaces brake fluid from the displacement chamber 25 through the opening exhaust valve 27 into the radial gap 32, from which the brake fluid flows through the annular gap 33 in the pump outlet 34.
  • the stepped piston 4 defines an annular space in the bushing 3, which is referred to here as step room 36.
  • a volume of the step room 36 increases in a forward stroke of the stepped piston 4, in which the volume of the displacement chamber 25 decreases, and the volume of the step room 36 decreases during the return stroke of the stepped piston 4, in which the volume of the displacement chamber 25 increases.
  • a cross-sectional area of the annular step space 36 is smaller than the cross-sectional area of the displacement space 25, the volume change of the step space 36 at a stroke of the stepped piston 4 is smaller than the inverse volume change of the displacement space 25.
  • a cross-sectional ratio of 2: 1 so that the volume changes of the displacement space 25 and the step room 36 are in a ratio of 2: 1.
  • the step room 36 communicates through a valve 37 with the annular bushing 33 enclosing the bushing 3 and thereby with the pump outlet 34.
  • brake fluid displaces from the displacement space 25 into the pump outlet 34
  • the piston pump 1 sucks brake fluid out of the annular gap 33 or the pump outlet 34 in the step room 36.
  • the sucked in a forward stroke in the step room 36 Brake fluid volume is smaller than the simultaneously displaced from the displacement chamber 25 brake fluid volume, so that the piston pump 1 displaces a total of brake fluid into the pump outlet 34.
  • the outlet valve 27 is closed and the stepped piston 4 displaces brake fluid from the step space 36, which reduces the return stroke, into the pump outlet 34, so that the piston pump 1 also displaces brake fluid into the pump outlet 34 during the return stroke.
  • the amount of brake fluid displaced from the displacement space 25 during a forward stroke of the stepped piston 4 is twice as large as the amount of brake fluid drawn in the step space 36, thereby equaling the amount of brake fluid displaced in the pump outlet 34 during a forward stroke and the return stroke from the piston pump 1 as a whole is.
  • the piston pump 1 Due to the step space 36 and the outlet or pressure side stepped design of the stepped piston 4, the piston pump 1 has a more uniform outlet volume flow, which is distributed over the forward stroke and the return stroke; Pressure pulsations in the pump outlet 34 and thus on the pressure side of the piston pump 1 are reduced.
  • the valve 37 associated with the step chamber 36 is a check valve or a differential pressure valve, which is held open by a valve spring 38 and closes when a pressure difference between the pump outlet 34 and the step room 36 a closing pressure of the valve 37th exceeds.
  • the valve 37 can also be understood as a pressure-controlled valve.
  • the closing pressure of the valve 37 is for example 40 bar. If the differential pressure between the pump outlet 34 and the step room 36 exceeds the closing pressure of the valve 37, the valve 37 closes and thereby hydraulically separates the step room 36 from the pump outlet 34.
  • the eccentric remote piston stage 8 of the stepped piston 4 works maximally against the closing pressure of the valve 37, which a force for moving the stepped piston 4 in the return stroke, which must be applied by the piston spring 6 limited.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
EP15767111.6A 2014-09-19 2015-09-09 Kolbenpumpe Active EP3194772B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014218915.2A DE102014218915A1 (de) 2014-09-19 2014-09-19 Kolbenpumpe
PCT/EP2015/070562 WO2016041821A1 (de) 2014-09-19 2015-09-09 Kolbenpumpe

Publications (2)

Publication Number Publication Date
EP3194772A1 EP3194772A1 (de) 2017-07-26
EP3194772B1 true EP3194772B1 (de) 2018-12-26

Family

ID=54151255

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15767111.6A Active EP3194772B1 (de) 2014-09-19 2015-09-09 Kolbenpumpe

Country Status (7)

Country Link
US (1) US10385833B2 (ko)
EP (1) EP3194772B1 (ko)
JP (1) JP6453471B2 (ko)
KR (1) KR102366884B1 (ko)
CN (1) CN106715900B (ko)
DE (1) DE102014218915A1 (ko)
WO (1) WO2016041821A1 (ko)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NO20171100A1 (en) * 2017-07-04 2019-01-07 Rsm Imagineering As A dual-acting pressure boosting liquid partition device, system, fleet and use
CN110481528B (zh) * 2018-10-24 2020-11-06 京西重工（上海）有限公司 液压控制单元
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
CN115143096B (zh) * 2022-09-06 2022-12-02 万向钱潮股份公司 一种汽车电子稳定控制系统用柱塞泵

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
GB8522466D0 (en) * 1985-09-11 1985-10-16 British Syphon Ind Plc Liquid dispence system
DE4102364A1 (de) 1991-01-28 1992-07-30 Teves Gmbh Alfred Kolbenpumpe
DE19813302A1 (de) * 1998-03-26 1999-09-30 Bosch Gmbh Robert Kolbenpumpe bzw. Bremsanlage mit Kolbenpumpe
DE19924774A1 (de) * 1999-05-29 2000-11-30 Bosch Gmbh Robert Kolbenpumpe
DE102004061810A1 (de) 2004-12-22 2006-07-06 Robert Bosch Gmbh Kolbenpumpe mit wenigstens einem Stufenkolbenelement
DE102006051589A1 (de) * 2006-11-02 2008-05-08 Robert Bosch Gmbh Kolbenpumpe
DE102006061462B4 (de) * 2006-12-23 2015-11-12 Continental Teves Ag & Co. Ohg Elektrohydraulisches Pumpensystem
DE102010063544A1 (de) * 2010-12-20 2012-06-21 Robert Bosch Gmbh Kolbenpumpe, insbesondere für eine hydraulische Fahrzeugbremsanlage
CN103670989A (zh) * 2014-01-13 2014-03-26 四川大学 对置活塞泵

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
KR20170058372A (ko) 2017-05-26
KR102366884B1 (ko) 2022-02-25
EP3194772A1 (de) 2017-07-26
US20170291586A1 (en) 2017-10-12
WO2016041821A1 (de) 2016-03-24
DE102014218915A1 (de) 2016-04-07
CN106715900A (zh) 2017-05-24
JP6453471B2 (ja) 2019-01-16
CN106715900B (zh) 2019-05-31
US10385833B2 (en) 2019-08-20
JP2017526864A (ja) 2017-09-14

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