EP2823176A1 - Soupape de dosage d'un fluide - Google Patents

Soupape de dosage d'un fluide

Info

Publication number
EP2823176A1
EP2823176A1 EP13702796.7A EP13702796A EP2823176A1 EP 2823176 A1 EP2823176 A1 EP 2823176A1 EP 13702796 A EP13702796 A EP 13702796A EP 2823176 A1 EP2823176 A1 EP 2823176A1
Authority
EP
European Patent Office
Prior art keywords
channel
valve
flow channel
fluid
valve according
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.)
Granted
Application number
EP13702796.7A
Other languages
German (de)
English (en)
Other versions
EP2823176B1 (fr
Inventor
Michael Mayer
Pablo Antonio NAPAL JIMENEZ
Michael Fischer
Andrej Elsinger
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 EP2823176A1 publication Critical patent/EP2823176A1/fr
Application granted granted Critical
Publication of EP2823176B1 publication Critical patent/EP2823176B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the invention is based on a valve for metering a fluid, in particular for injecting fuel in a fuel injection system of internal combustion engines, according to the preamble of claim 1.
  • a known valve for metering a fluid (DE 10 2009 026 532 A1) has an inlet for the fluid accommodated in a connection piece, an orifice formed in a valve body for metering a metered quantity of fluid by means of a piezoelectric actuator closing and releasing the metering opening a valve closing spring controlled valve needle and a leading from the inlet to the orifice,
  • a valve housing Coaxially with the valve housing, an elongate sleeve extends between the connection piece and the valve body.
  • the sleeve is fastened to the connection piece and the valve body with its two sleeve ends and accommodates a valve assembly consisting of the piezoelectric actuator and a hydraulic coupler.
  • the annular gap remaining between the sleeve and the valve housing constitutes the hollow-cylindrical flow channel for the fluid, so that the inner channel wall of the flow channel is formed by the sleeve and the outer channel wall of the flow channel by the valve housing.
  • a valve chamber In the valve body of the orifice is a valve chamber
  • valve according to the invention with the features of claim 1 has the advantage that by dividing the flow channel into several
  • Flow connection between the successive channel sections in the flow direction-related hydraulic resonances can be influenced so that an excitation critical, installation-based Strukurmoden no longer occurs, so hydraulic resonances in the critical frequency range of typically 3 kHz can no longer arise.
  • the subdivision of the flow channel and the production of the flow connection between the channel sections is realized in that at least one channel location in the flow channel, a ring with an annular gap and one of the radial channel width corresponding ring thickness or ring thickness or radial annular wall dimension is inserted into the flow channel ,
  • a ring advantageously has one rectangular or circular cross section and is made of a band or wire with a rectangular or circular cross section.
  • the ring is fixed in the flow channel, which is preferably done by positive immersion of the ring in at least one annular groove which is incorporated in the inner and / or outer channel wall of the flow channel.
  • the rings are aligned so that their annular gaps are rotated against each other in the circumferential direction, preferably by 180 °.
  • This constructive arrangement of the rings has the advantage that between two successive channel sections, an intermediate volume of the fluid is generated.
  • the subdivision of the flow channel and the flow connection between the generated channel sections is realized in that at least one point in the
  • Flow channel is made a cross-sectional constriction.
  • Cross-sectional constriction is advantageously achieved by protruding from at least one of the two channel walls of the flow channel, a circumferential on the channel wall nose into the flow channel, which is preferably made by a recess incorporated in the channel wall.
  • a circumferential constriction of the flow cross section of the flow channel has the advantage that, depending on the fluid pressure, the cross section of the constriction changes, namely increases with increasing pressure.
  • the cross section of the constriction changes, namely increases with increasing pressure.
  • the operating points with high pressure are generally not critical for noise generation and need no anyway
  • FIG. 1 shows a longitudinal section of a valve for metering a fluid
  • FIG. 2 is an enlarged view of section A in FIG. 1,
  • FIG. 3 is an enlarged view of the detail A according to a second embodiment with an in-flow channel ring with a rectangular ring cross section,
  • FIG. 4 shows a perspective view of the ring in FIG. 3,
  • FIG. 5 is an enlarged view of the detail A in Figure 1 according to a third embodiment with an in-flow channel ring with a circular ring cross section,
  • FIG. 6 shows a perspective view of the ring according to FIG. 5
  • Figure 7 is an enlarged view of the detail A in Figure 1 according to a fourth embodiment with two at a short distance from each other in the
  • FIG. 8 shows a perspective view of the two rings according to FIG. 7.
  • FIG. 1 in longitudinal section valve for metering a fluid is preferably used as an injection valve for injecting fuel in a fuel injection system of internal combustion engines, wherein
  • the fuel is injected into the combustion cylinder of the internal combustion engine.
  • the valve has an inlet 1 1 for the fluid, a
  • the flow channel 13 has an outer channel wall 13 a, which is formed by a tubular valve housing 14, and an inner channel wall 13 b, which is formed by a valve housing 14 concentrically arranged sleeve 15.
  • the valve housing 14 is closed fluid-tight at one end face of a connector 16 and at its other end face of a valve body.
  • the connecting piece 16 contains the inlet 1 1 while the metering opening 17 is formed in the valve body 17.
  • the sleeve 15 is with its one sleeve end to the connector 16 and with its other
  • valve assembly which consists of a kardanisch on the connector 16 mounted hydraulic coupler 18, a connected to the coupler 18 piezoelectric or magnetostrictive actuator 19 and a valve body 17 is supported valve closing spring 20.
  • valve 21 which is guided axially displaceably in the valve body 17 and controls the metering opening 12 with a closing head 22 which cooperates with a valve seat 23 surrounding the metering opening 12.
  • the actuator 19 is connected via a contact bridge 24 with an electrical
  • Connector 25 is connected and lifts when energized the closing head 22 of the valve needle 21 against the restoring force of the valve closing spring 20 from the valve seat 23 to the outside.
  • the valve-closing spring 20 which is tensioned when the orifice 12 is opened via the valve needle 21, pushes the closing head 22 back onto the valve seat 23, so that the orifice 12 is closed.
  • the connection of the flow channel 13 and the metering opening 12 is within the valve body 17 by one of the metering opening 12 upstream valve chamber 26 and one of the flow channel 13 for
  • Connecting bore 33 is connected to the inlet 1 1.
  • the flow channel 13 is annular
  • Channel sections 131, 132 divided and made a flow connection for the fluid between the channel sections 131, 132.
  • the subdivision of the flow channel 13 in the divider ratio is 1: 1. But according to a desired frequency shift can also others Division ratios and the subdivision of the flow channel 13 may be required in more than two channel sections.
  • the subdivision of the flow channel 13 into two or more channel sections and the production of the flow connection between the channel sections can be realized at one or more channel locations in various ways.
  • a cross-sectional constriction of the annular cross-section of the flow channel 13 is made at a channel location in the flow channel 13.
  • annular recess 28 is impressed, which results in a projecting into the flow channel 13, on the channel wall 13a circumferential nose 29.
  • the same nose 29 may alternatively be formed on the sleeve 15 formed by the inner
  • Channel wall 13b be present.
  • the arrangement of a respective nose 29 on the inner channel wall 13b and on the outer channel wall 13a is possible, wherein the lugs 29 are opposite to each other or may be offset from each other at a short distance.
  • the width of the nose 29 seen in the axial direction can be adjusted according to the degree of desired throttling.
  • Widths are 1 -10 mm.
  • the remaining in the radial direction width of the flow channel 13 at the channel location can also be adjusted according to the desired degree of throttling or narrower.
  • Typical gap widths are 0.01 - 0.1 mm.
  • FIGS. 3 to 8 Three further exemplary embodiments are illustrated in FIGS. 3 to 8, as a subdivision into two consecutive channel sections 131 and 132 with a flow connection between the channel sections 131 and 132 is achieved at a channel location of the flow channel 13. In all three cases will be rings
  • Flow channel 13 corresponding ring thickness or ring thickness or radial annular wall dimension used, which are inserted into the flow channel 13.
  • Flow channel 13 corresponding ring thickness or ring thickness or radial annular wall dimension used, which are inserted into the flow channel 13.
  • Flow channel 13 corresponding ring thickness or ring thickness or radial annular wall dimension used, which are inserted into the flow channel 13.
  • Flow channel 13 corresponding ring thickness or ring thickness or radial annular wall dimension used, which are inserted into the flow channel 13.
  • Flow channel 13 corresponding ring thickness or ring thickness or radial annular wall dimension used, which are inserted into the flow channel 13.
  • Flow channel 13 corresponding ring thickness or ring thickness or radial annular wall dimension used, which are inserted into the flow channel 13.
  • the ring 30 is in Flow channel 13 fixed to at least one channel wall, wherein the fixation is effected in that the ring 30 partially inserted into at least one of the channel walls 13a, 13b incorporated annular groove 32 positively. in the
  • the ring 30 has a rectangular cross-section and the annular groove 32 is incorporated into the inner channel wall 13b.
  • the ring 30 is made of a band. in the
  • the ring 30 has a circular cross-section and the annular groove 32 is formed by an impressed from the inside of the outer channel wall 13a in the outer channel wall 13a, annular bead.
  • the ring 30 is made of a wire.
  • each ring 30 has a circular cross-section and partially immersed in an annular groove 32, each formed by an annular bead, which is embossed into the outer channel wall 13a from the inside thereof.
  • the rings 30 are aligned in such a way that their annular gaps 31
  • Channel portions an intermediate volume of the fluid is generated.
  • the same effect is achieved by the above-mentioned arrangement of two lugs 29 on the outer and inner channel wall 13a 13b, which are offset from each other at a short distance.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Valves (AREA)
  • Lift Valve (AREA)

Abstract

L'invention concerne une soupape de dosage d'un fluide, destinée en particulier à injecter du carburant dans un dispositif d'injection de carburant de moteurs à combustion interne, qui comporte une arrivée (11) pour le fluide, une ouverture de dosage (12) pour le fluide et un canal d'écoulement (13) de forme cylindrique creuse, s'étendant en longueur, menant de l'arrivée (11) à l'ouverture de dosage (12) et pourvu d'une paroi extérieure (13a) et d'une paroi intérieure (13b). L'invention vise à agir sur les résonances hydrauliques liées à la construction, de manière à ce qu'une excitation de modes structuraux critiques, liés au montage, ne puisse plus avoir lieu. A cet effet, le canal d'écoulement est divisé en au moins deux sections de canal (131, 132) séparées l'une de l'autre, et une liaison fluidique étranglée pour le fluide est établie entre des sections de canal (131, 132) successives.
EP13702796.7A 2012-03-07 2013-01-30 Soupape de dosage d'un fluide Not-in-force EP2823176B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012203607A DE102012203607A1 (de) 2012-03-07 2012-03-07 Ventil zum Zumessen eines Fluids
PCT/EP2013/051803 WO2013131691A1 (fr) 2012-03-07 2013-01-30 Soupape de dosage d'un fluide

Publications (2)

Publication Number Publication Date
EP2823176A1 true EP2823176A1 (fr) 2015-01-14
EP2823176B1 EP2823176B1 (fr) 2017-04-19

Family

ID=47666131

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13702796.7A Not-in-force EP2823176B1 (fr) 2012-03-07 2013-01-30 Soupape de dosage d'un fluide

Country Status (8)

Country Link
US (1) US20150028136A1 (fr)
EP (1) EP2823176B1 (fr)
JP (1) JP5933766B2 (fr)
KR (1) KR20140133851A (fr)
CN (1) CN104350269B (fr)
DE (1) DE102012203607A1 (fr)
RU (1) RU2629851C2 (fr)
WO (1) WO2013131691A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014222448A1 (de) 2014-11-04 2016-05-04 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102014222454A1 (de) 2014-11-04 2016-05-04 Robert Bosch Gmbh Brennstoffeinspritzventil

Family Cites Families (26)

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Publication number Priority date Publication date Assignee Title
SU798340A2 (ru) * 1974-06-04 1981-01-23 Коломенский Филиал Всесоюзногозаочного Политехнического Института Форсунка с гидравлическим запира-НиЕМ иглы
JPH0515572Y2 (fr) * 1987-03-28 1993-04-23
JP3525613B2 (ja) * 1996-02-21 2004-05-10 いすゞ自動車株式会社 内燃機関の燃料噴射装置
DE19640782A1 (de) * 1996-10-02 1998-04-09 Bosch Gmbh Robert Ventil und Verfahren zur Herstellung eines Ventiles
JP3821179B2 (ja) * 1997-07-30 2006-09-13 三菱ふそうトラック・バス株式会社 燃料噴射装置
DE19912665A1 (de) * 1999-03-20 2000-09-21 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19932760A1 (de) * 1999-07-14 2001-01-18 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19932763A1 (de) * 1999-07-14 2001-01-18 Bosch Gmbh Robert Brennstoffeinspritzventil
WO2002036959A2 (fr) * 2000-11-02 2002-05-10 Siemens Aktiengesellschaft Dispositif de dosage de liquide comprenant une zone d'etranglement
US6439201B1 (en) * 2000-12-20 2002-08-27 Caterpillar Inc. Fuel injector having dual flow rate capabilities and engine using same
DE10121892A1 (de) * 2001-05-05 2002-11-07 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
US6629650B2 (en) * 2001-07-10 2003-10-07 Delphi Technologies, Inc. Fuel injector with integral damper
WO2003016707A1 (fr) * 2001-08-08 2003-02-27 Siemens Aktiengesellschaft Dispositif de dosage
DE10148824A1 (de) * 2001-10-04 2003-04-10 Bosch Gmbh Robert Brennstoffeinspritzventil
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DE102005036444A1 (de) * 2005-08-03 2007-02-08 Robert Bosch Gmbh Einspritzdüse
JP2007270682A (ja) * 2006-03-30 2007-10-18 Honda Motor Co Ltd エンジン側燃料配管およびタンク側燃料配管を備える燃料供給装置
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EP2218900B1 (fr) * 2009-02-16 2011-09-28 Continental Automotive GmbH Ensemble de soupape pour soupape d'injection et soupape d'injection
DE102009026532A1 (de) 2009-05-28 2010-12-02 Robert Bosch Gmbh Einspritzventil für ein Fluid
US8317112B2 (en) * 2010-01-25 2012-11-27 Continental Automotive Systems Us, Inc. High pressure fuel injector seat that resists distortion during welding
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Also Published As

Publication number Publication date
CN104350269B (zh) 2017-09-15
JP2015508861A (ja) 2015-03-23
JP5933766B2 (ja) 2016-06-15
KR20140133851A (ko) 2014-11-20
WO2013131691A1 (fr) 2013-09-12
CN104350269A (zh) 2015-02-11
US20150028136A1 (en) 2015-01-29
EP2823176B1 (fr) 2017-04-19
DE102012203607A1 (de) 2013-09-12
RU2014140230A (ru) 2016-04-27
RU2629851C2 (ru) 2017-09-04

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