EP2655882A1 - Pompe équipée d'un étranglement - Google Patents

Pompe équipée d'un étranglement

Info

Publication number
EP2655882A1
EP2655882A1 EP11778826.5A EP11778826A EP2655882A1 EP 2655882 A1 EP2655882 A1 EP 2655882A1 EP 11778826 A EP11778826 A EP 11778826A EP 2655882 A1 EP2655882 A1 EP 2655882A1
Authority
EP
European Patent Office
Prior art keywords
pump
spring element
outflow channel
throttle
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11778826.5A
Other languages
German (de)
English (en)
Inventor
Horst Beling
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 EP2655882A1 publication Critical patent/EP2655882A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing

Definitions

  • the invention relates to a pump having an outflow channel for discharging fluid from the pump whose passage area is determined by a throttle.
  • a throttle is often arranged in the outflow or outflow.
  • the throttle is intended to reduce the effect of pressure pulsations in the pump on the subsequent hydraulic system and in particular to reduce the noise of the pump.
  • noise reduction such chokes are known with fixed passage area.
  • Typical pumps for automotive brake systems comprise a cylinder in which a piston is slidably mounted. When moving the piston promotes a fluid in the form of brake fluid in the discharge channel of the pump.
  • a pump is provided with an outflow channel for discharging fluid from the pump, whose passage area is determined by a throttle.
  • the throttle is designed with a passage area of the outflow channel changing in size spring element.
  • the passage area of the throttle is made variable at an outflow channel of a pump.
  • the throttle effect can be adapted to the operating situation of the pump.
  • the variation of the size of the passage area is created in a particularly simple and cost-producible manner by means of a deflectable spring element.
  • the spring element is loaded by the hydraulic pressure generated by the pump and deviates correspondingly. With the retreat, the spring element increases at the same time the passage area, so that the throttle effect decreases.
  • the throttle effect is reduced at high flow rate of the pump, whereas the throttling effect is stronger at low flow rate.
  • the passage area of the pump is designed with a non-closable by the spring element bypass surface.
  • the bypass surface forms an always permeable passage area or cross-sectional area in the discharge channel. It thereby ensures a minimum outflow from the pump.
  • the bypass surface is preferably formed next to the spring element along its direction of movement.
  • the bypass surface is preferably designed as a gap, slot or the like next to the spring element. This gap is not closed and can therefore always be flowed through freely. Furthermore, the gap serves as tolerance compensation with regard to the dimensional tolerances of the width of the spring element and the width of the outflow channel. As a result, the assembly of the spring element in the discharge channel is easier.
  • the spring element is designed with a leaf spring in the pump.
  • the spring element in the outflow channel can be arranged particularly easily and positioned in a fixed manner. Furthermore, there is only a small space requirement for the leaf spring.
  • a plate spring can be selected as a spring element.
  • a diaphragm spring allows a large range of variation in terms of the size of the passage area with largely closed and largely open Mandarinskyse.
  • the leaf spring is preferably configured and arranged such that it protrudes arcuately into the outflow channel. The curved shape of the leaf spring can then be targeted by the fluid flowing through the discharge channel, whereby turbulence formation can be minimized. Such a flowed leaf spring thus deviates back defined due to the pressure force of the flow.
  • the size of the passage area and thus the throttle effect is precisely changed in this way. Thus, a defined flow situation can be generated on the spring element, which leads to a correspondingly defined throttle behavior of the variable throttle according to the invention.
  • the leaf spring is furthermore preferably located with at least one section on a wall of the outflow channel and is rounded at this section.
  • the thus configured leaf spring can be positioned by simply inserting or applying in the interior of the discharge channel.
  • the at least one rounded portion reduces the friction of such a leaf spring applied to the wall of the outflow channel. Consequently, the bending behavior of the leaf spring is improved when it is pushed back by the pressure force of the inflowing hydraulic fluid and thereby deformed.
  • At least one shoulder is preferably formed, with which the spring element is positioned in the longitudinal direction of the outflow channel.
  • the shoulder prevents migration of the spring element along the Ausströmkanals.
  • a pump cover is provided on the pump, which acts as a particular disc-shaped cover member for the cylinder of the pump and has a cylinder facing end face.
  • the outflow channel is formed with the spring element disposed therein end face.
  • the spring element is laterally easy to install or to install.
  • the frontal tig formed outflow to a closed channel shape or tube shape are designed.
  • the pump is formed along a cylinder axis and the outflow channel aligned with the spring element arranged therein radially to the cylinder axis.
  • the described pump is used in a motor vehicle brake system.
  • the inventively achieved, variable throttle effect is particularly advantageous for use in motor vehicle systems and the targeted there noise reduction.
  • Fig. 1 is a longitudinal section of a pump according to the invention.
  • Fig. 2 shows the section II - II of FIG. 1 in an enlarged view.
  • a pump 10 is illustrated, in which in a substantially block-shaped housing 1 1, a first piston member 12 and a second piston member 13 are slidably mounted.
  • the piston elements 12 and 13 are coupled to one another in a force-transmitting manner, in particular connected on the front side, and are driven by means of a drive 14 in the form of an eccentric.
  • the piston member 13 is biased against the drive 14 with a spring 16 in the form of a helical spring.
  • the spring 16 is arranged in a delivery chamber 18 which is surrounded by a cylinder 19. In the cylinder 19, the piston member 13 slides fluid-tight along.
  • An inlet 20 is fluidly connected to an inlet port 28 formed centrally in the piston member 13 with respect to the longitudinal axis of the assembly.
  • This inlet opening 28 is part of an inlet valve 22 and, as such, cooperates with a closure body 24 to selectively allow brake fluid to flow into the delivery space 18.
  • the inlet valve 22 is designed as a check valve, the closure body 24 being in the form of a ball. is formed, which is biased by a spring 26 against the inlet opening 28.
  • an outlet opening 36 is located centrally on an end face of the cylinder 19 facing away from the inlet opening 28.
  • This outlet opening 36 is part of an outlet valve 30 and interacts with a spherical closure body 32.
  • the closure body 32 is biased by a spring 34 against the outlet opening 36.
  • the outlet valve 30 is thus also designed as a check valve.
  • a pump cover 37 is arranged behind the outlet opening 28 (and thus outside of the delivery chamber 18) on the front side of the cylinder 19.
  • the pump cover 37 is placed on the front end of the cylinder 19 and supports the spring 34 from. Further, the pump cover 37 optionally provides sufficient space for a reservoir or damper (not shown).
  • an outflow 38 formed, in particular milled, which leads to an outlet 40 on the housing 1 1.
  • a throttle spring element 42 is arranged in the form of a leaf spring.
  • the leaf spring is shaped in such a way that in its rest position it essentially closes off the outflow channel 38 and can be deformed by an influx with escaping brake fluid in order then to provide an enlarged passage area in the outflow channel 38 in comparison to the rest position.
  • the leaf spring has an overall arc-shaped cross-sectional shape (see FIG. 1) and is provided at its end regions with in each case an oppositely curved or rounded section 46.
  • the sections 46 lie against one of the walls of the outflow channel 38, which are formed by the pump cover 37 at.
  • the leaf spring is thus similar to a Greek Omega ( ⁇ ) bent.
  • the bent portions 46 reduce the friction of the leaf spring at the bearing or contact surfaces in the discharge channel 38th
  • the width (measured in the circumferential direction of the pump cover 37) of the leaf spring is adapted to the width of the outflow channel 38, that on both sides of the Leaf spring a gap 54 remains.
  • the gaps 54 thus extend along the direction of movement of the spring element 42 and form a bypass line or a minimum passage area for the outflow channel 38, with which a resistance-free minimum outflow from the pump 10 is ensured. Furthermore, the gaps 54 serve as tolerance compensation with regard to the width dimensions mentioned.
  • a shoulder 44 is formed as a kind of stage in the outflow channel. At this shoulder 44 is located on a portion 46 of the spring element 42, which prevents the spring element 42 could migrate radially or slip. In particular, it is prevented that the spring element 42 could migrate (due to pressure pulsations in the outflow channel 44) in the direction of the outlet valve 30.
  • the outflow channel 38 is divided from the inside to the outside into a first, radial section 48, a second, radial section 50 and a third, axial section 52.
  • the shoulder 44 is formed in the section 48 and the spring element 42 in the section 50.
  • the transition from the section 50 to the section 52 is L-shaped, whereby the spring element 42 is retained in the direction of the outlet 40.
  • the portion 48 is designed slightly longer than the leaf spring, so that this finds sufficient space for their bending movement.
  • variable throttle created by the spring element 42 When a pumping action, triggered by the drive 14 which pushes the coupled piston elements 12 and 13 into the delivery chamber 18, takes place, fluid is forced under pressure through the outlet valve 30 pushed in the outflow channel 38.
  • the fluid can flow through the gaps 54 through the outflow channel 38.
  • a dynamic pressure builds up in front of the spring element 42, which results in that the spring element 42 is moved from its rest position into a deformed position. In this deformed position, the spring element 42 is less curved, ie bent back. It then no longer largely obstructs the outflow channel 38, but instead releases an enlarged passage area through which fluid can reach the outlet 40.
  • the spring element 42 is thus deformed as soon as a larger amount of fluid is conveyed out of the partial region 48 of the outflow channel 38.
  • the deformation begins only from a certain pressure value or from a certain force which exerts the fluid on the spring element 42. It increases the flow cross-section through the discharge channel 38, which was previously largely closed.
  • the throttle thus regulates the flow of the fluid through the discharge channel 38 as a function of the delivery rate of the pump 10.
  • the spring element 42 can be produced inexpensively as a simple sheet metal bent part by means of stamping. In addition, only a small footprint for the spring element 42 is necessary. In principle, only one outflow channel 38 with an associated variable throttle is necessary. However, it is also possible for a plurality of such outflow channels to be distributed, in particular distributed on the circumference of the pump cover 37.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Regulating Braking Force (AREA)

Abstract

L'invention porte sur une pompe (10) possédant un canal de sortie (38) servant à évacuer du fluide de la pompe (10), dont l'aire de passage est déterminée par un étranglement. Selon l'invention, l'étranglement est réalisé avec un élément élastique (42) qui fait varier la dimension de l'aire de passage d'étranglement du canal de sortie (38).
EP11778826.5A 2010-12-23 2011-10-24 Pompe équipée d'un étranglement Withdrawn EP2655882A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010064114.6A DE102010064114B4 (de) 2010-12-23 2010-12-23 Pumpe mit einer Drossel
PCT/EP2011/068566 WO2012084307A1 (fr) 2010-12-23 2011-10-24 Pompe équipée d'un étranglement

Publications (1)

Publication Number Publication Date
EP2655882A1 true EP2655882A1 (fr) 2013-10-30

Family

ID=44906054

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11778826.5A Withdrawn EP2655882A1 (fr) 2010-12-23 2011-10-24 Pompe équipée d'un étranglement

Country Status (6)

Country Link
US (1) US9303639B2 (fr)
EP (1) EP2655882A1 (fr)
JP (1) JP5786032B2 (fr)
CN (1) CN103282654B (fr)
DE (1) DE102010064114B4 (fr)
WO (1) WO2012084307A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010040157A1 (de) * 2010-09-02 2012-03-08 Robert Bosch Gmbh Kolbenpumpe zur Förderung von Fluiden und zugehörige Fahrzeugbremsanlage
DE102012213022A1 (de) * 2012-07-25 2014-01-30 Robert Bosch Gmbh Vorrichtung zur Drosselung einer Fluidströmung und korrespondierende Kolbenpumpe zur Förderung von Fluiden
UA119134C2 (uk) 2012-08-08 2019-05-10 Аарон Фьюстел Роторні пристрої з розширюваними камерами, що мають регульовані проходи для робочого плинного середовища, а також системи, що мають такі пристрої
DE102014220368A1 (de) * 2014-10-08 2016-04-14 Robert Bosch Gmbh Kolbenpumpe für eine hydraulische Fahrzeugbremsanlage
CN108730087B (zh) * 2017-04-24 2022-05-27 卡特彼勒公司 抑制空化的液体泵

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2919229A1 (de) * 1979-05-12 1980-11-13 Inst Motorenbau Prof Huber E V Kraftstoff-foerderpumpe fuer einspritzsysteme mit kontinuierlicher kraftstofffoerderung und intermittierender einspritzung
DE3706028A1 (de) * 1986-03-07 1987-09-10 Zahnradfabrik Friedrichshafen Radialkolbenpumpe
CH674243A5 (fr) 1987-07-08 1990-05-15 Dereco Dieselmotoren Forschung
SE9101852A0 (sv) * 1991-06-17 1992-12-18 Gustavsberg Vårgårda Armatur Ab Blandarventil av enspakstyp försedd med anordning för att förebygga tryckstöt vid spakens stängningsrörelse
DK122894A (da) 1994-10-24 1996-04-25 Danfoss Compressors Gmbh Trykventil kom kompressor
DE19732792A1 (de) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Kolbenpumpe
DE19732791A1 (de) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Kolbenpumpe
JP2000053010A (ja) * 1998-08-07 2000-02-22 Bosch Braking Systems Co Ltd ステアリングダンパ
DE19928913A1 (de) * 1999-06-24 2001-01-04 Bosch Gmbh Robert Kolbenpumpe
DE10016895B4 (de) * 2000-04-05 2008-05-08 Continental Teves Ag & Co. Ohg Hydraulikblock mit mindestens einer Pumpe
US7004733B2 (en) * 2001-06-30 2006-02-28 Robert Bosch Gmbh Piston pump
DE10212136C1 (de) * 2002-03-19 2003-10-30 Siemens Ag Spülventil
DE102005016271A1 (de) * 2005-04-08 2006-11-09 Valeo Compressor Europe Gmbh Verdichter
DE102007047418A1 (de) * 2007-10-04 2009-04-23 Robert Bosch Gmbh Kolbenpumpe zur Förderung eines Fluids und zugehöriges Bremssystem
DE102007049152A1 (de) * 2007-10-12 2009-04-16 Robert Bosch Gmbh Hydraulische Kolbenpumpe
DE102010040169A1 (de) 2010-09-02 2012-03-08 Robert Bosch Gmbh Vorrichtung zur Drosselung einer Fluidströmung und korrespondierende Kolbenpumpe zur Förderung von Fluiden

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012084307A1 *

Also Published As

Publication number Publication date
CN103282654B (zh) 2016-04-13
CN103282654A (zh) 2013-09-04
DE102010064114A1 (de) 2012-06-28
DE102010064114B4 (de) 2021-07-29
JP5786032B2 (ja) 2015-09-30
US9303639B2 (en) 2016-04-05
WO2012084307A1 (fr) 2012-06-28
JP2014503742A (ja) 2014-02-13
US20140003982A1 (en) 2014-01-02

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