EP0859910A1 - Soupape, en particulier soupape d'injection de carburant - Google Patents

Soupape, en particulier soupape d'injection de carburant

Info

Publication number
EP0859910A1
EP0859910A1 EP97942763A EP97942763A EP0859910A1 EP 0859910 A1 EP0859910 A1 EP 0859910A1 EP 97942763 A EP97942763 A EP 97942763A EP 97942763 A EP97942763 A EP 97942763A EP 0859910 A1 EP0859910 A1 EP 0859910A1
Authority
EP
European Patent Office
Prior art keywords
swirl
valve
valve according
generating means
outlet opening
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
EP97942763A
Other languages
German (de)
English (en)
Other versions
EP0859910B1 (fr
Inventor
Norbert Keim
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 EP0859910A1 publication Critical patent/EP0859910A1/fr
Application granted granted Critical
Publication of EP0859910B1 publication Critical patent/EP0859910B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1853—Orifice plates
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S239/00—Fluid sprinkling, spraying, and diffusing
    • Y10S239/90—Electromagnetically actuated fuel injector having ball and seat type valve

Definitions

  • Valve in particular fuel injector
  • the invention is based on a valve, in particular a fuel injector, according to the preamble of the main claim.
  • a valve in particular a fuel injection valve, is already known from EP-OS 0 057 407, which has a swirl body following a valve closing body upstream of a spray opening, through which a swirl component is applied to the fuel to be sprayed.
  • the swirl flow thus created is said to cause better swirling of the fuel, as a result of which finer atomization of the fuel is achieved compared to line jet spraying.
  • a fuel injector is also known from JP-OS 57-183559, which has a swirling device upstream of an outlet opening of the valve.
  • This swirling device has a multiplicity of spiral grooves, all of which have the same orientation and serve to apply a swirl component to the fuel for improved swirling.
  • the Atomization of the fuel can also be improved by tangential air supply channels, with which the air is also swirled.
  • swirl channels, swirl grooves or other swirl devices on valves which, for. B. are provided directly on the valve needle or on the valve closing body, that is also upstream of the valve seat surface. All these known swirl arrangements have in common that the entire fluid to be sprayed is influenced by the swirl elements only in one direction or orientation.
  • Injection valve is provided on the injection side.
  • the fluid to be sprayed emerges from an outlet opening of the injection valve and then flows through the atomizer arrangement, which is supplied with air via air lines.
  • the atomizer arrangement contains two axially successive vortex planes into which air is blown.
  • the vortex planes are designed so that the two air vortices to be formed have an opposite direction of rotation.
  • the fluid in particular a fuel, is also entrained and partially twisted by the swirling air, but this can only be achieved by the energy stored in the air. Due to the opposite directions of rotation of the vortex flows, the rotary movement of the total flow is canceled again when it emerges from the atomizer arrangement.
  • the valve according to the invention in particular fuel injection valve with the characteristic features of the main claim has the advantage that the atomization quality of a fluid to be sprayed and finely atomized, in particular fuel, can be further improved in a simple and cost-effective manner without additional auxiliary energy.
  • this is achieved in that swirl-generating means are provided on the valve downstream of the valve seat in such a way that at least two main flows are formed which are at least partially radially offset from one another and thus also flow through at least one outlet opening of the valve.
  • the two main currents have a different direction of direction. Due to the different orientation, large shear forces occur in the contact area of the two flows, which have a positive influence on the atomization.
  • the high opposing speeds of the individual flows cause swirl-induced shear forces in the fluid, which cause turbulence and turbulence.
  • the valve as a fuel injection valve, the exhaust gas emission of an internal combustion engine and the consumption of fuel can be reduced in an advantageous manner.
  • the swirl-generating means are advantageously provided as swirl attachments directly on a perforated disk.
  • Swirl channels projecting tangentially into an inner flow region of the swirl attachment are expediently arranged in at least two axially successive layers, with different radial ones in the individual layers Distances of the swirl channels to the longitudinal axis of the valve are present.
  • the swirl channels differ in their orientation from one position to another. With such an arrangement, radially nested, oppositely flowing fluids can be generated very easily
  • FIG. 1 shows a partially shown valve with swirl-generating means according to the invention
  • FIGS. 2a and 2b show idealized schematic diagrams of flow profiles in an outlet opening
  • FIG. 3 shows a section through a first example of swirl-generating means along the line III-
  • Figure 4 is a section through a second example of swirl-generating means along the line IV
  • FIG. 5 is a plan view of a first example of swirl-generating means
  • Figure 6 shows a third example of swirl-generating means in the form of a swirl attachment
  • Figure 7 shows a section through the swirl attachment along the line VII-VII in Figure 6
  • Figure 8 fourth example of swirl-generating means in the form of a swirl attachment
  • FIG. 9 shows a schematically illustrated, idealized speed distribution in the outlet opening of the swirl attachment according to FIG. 6.
  • the injection valve has a tubular valve seat support 1, in which a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2.
  • a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2.
  • a longitudinal opening 3 is a z.
  • the injection valve is actuated in a known manner, for example electromagnetically.
  • An indicated electromagnetic circuit with a magnet coil 10, an armature 11 and a core 12 is used for the axial movement of the valve needle 5 and thus for opening against the spring force of a return spring (not shown) or closing the injection valve.
  • the armature 11 is facing away from the valve closing body 7 End of the valve needle 5 by z.
  • a guide opening 15 of a valve seat body 16 is used to guide the valve closing body 7 during the axial movement.
  • the longitudinal opening 3 of the z. B. cylindrical valve seat body 16 tightly mounted by welding.
  • the valve seat body 16 is provided with a z. B. pot-shaped trained perforated disc (or nozzle plate) 21 concentrically and firmly connected so that it bears directly on the valve seat body 16.
  • the perforated disc 21 for. B. introduced a central outlet opening 22 by punching, eroding or etching, through which a fluid is sprayed according to the invention, which has at least two flows with different directions. This flow property is achieved by swirl-generating means 23 arranged downstream of a valve seat surface 29, which are explained in detail below.
  • valve seat body 16 and the perforated disk 21 are connected, for example, by a circumferential and sealed first weld seam 25 which is formed by a laser. This type of assembly increases the risk of undesired deformation of the perforated disk 21 in its central region with the outlet opening 22 and those arranged there swirl generating means 23 avoided.
  • the perforated disk 21 is further connected to the wall of the longitudinal opening 3 in the valve seat support 1, for example by a circumferential and tight second weld seam 30.
  • the insertion depth of the valve seat part consisting of valve seat body 16 and cup-shaped perforated disk 21 or means 23 into the longitudinal opening 3 determines the size of the stroke of the valve needle 5, since the one end position of the valve needle 5 when the solenoid 10 is not excited due to the valve closing body 7 resting on the valve seat surface 29 of the valve seat body 16 is fixed.
  • the other end position of the valve needle 5 is determined when the solenoid 10 is excited, for example by the armature 11 resting on the core 12. The path between these two end positions of the valve needle 5 thus represents the stroke.
  • the spherical valve closing body 7 interacts with the valve seat surface 29 of the valve seat body 16 tapering in the direction of the truncated cone, which is formed in the axial direction between the guide opening 15 and the lower end face 17 of the valve seat body 16, namely upstream of the swirl-generating means 23.
  • the valve partially shown in FIG. 1 represents only an exemplary embodiment variant.
  • the swirl-generating means 23 according to the invention can also be used on valves which differ significantly therefrom.
  • FIGS. 2a and 2b show idealized schematic diagrams of the flow patterns desired according to the invention in an outlet opening 22, which, for. B. is introduced in the perforated disc 21.
  • a pot-shaped perforated disk 21 according to FIG. 1 is in no way required for flow profiles; rather, the perforated disks 21 or nozzle plates can be designed with completely different contours.
  • the outlet opening 22 can also be provided directly in the valve seat body 16 or in a nozzle holder.
  • the basic sketches illustrate that with the swirl-generating means 23 located upstream of the outlet opening 22, at least two flows of the fluid, in particular a fuel, are generated, which are largely independent of one another radially offset and thereby have a different direction of direction, the principal flow direction ⁇ spray direction) both subcomponents in the outlet opening 22 along the longitudinal valve axis 2 is the same as the arrows 32 are intended to indicate.
  • An inner flow component 33 regardless of the general axial flow direction 32, therefore has a direction that is different from the direction of an outer one, which is indicated by the broken line shown inner flow differs radially surrounding flow with an outer flow component 34.
  • FIG. 2a illustrates a flow principle in which the inner flow component 33 shown in dashed lines largely follows the axial flow direction 32, while the fluid around the inner flow region has an outer flow component 34, which is characterized by a swirling action.
  • the inner flow component 33 is thus flowed around in a circular, spiral manner by the outer flow component 34.
  • the inner flow component 33 in addition to the outer flow component 34, the inner flow component 33 also has a swirl, which, however, is in the opposite direction by means of the swirl-generating means 23
  • FIGS. 3 to 5 show embodiments of swirl-generating means 23 to achieve a flow principle according to Figure 2a;
  • FIGS. 6 to 9 represent examples of swirl-generating means 23 with which
  • FIGS. 3, 4 and 5 show two examples of swirl-generating means 23 which are designed as swirl elements on the perforated disk 21 and into a cylindrical opening region 35 of the valve seat body 16 following the valve seat surface 29 from the plane of the perforated disk 21 in the direction of the valve closing body 7 protrude into it.
  • a plan view (FIG. 5) of the swirl-generating means 23 in the region of the opening area 35 illustrates the shape and arrangement of the means 23 on the perforated disk 21, the Figures 3 and 4 are ultimately expanded sectional views along the line III-III and IV-IV in this plan view.
  • the swirl-generating means 23 are in the form of an arcuate arrangement arranged in a ring around the outlet opening 22
  • Guide elements 37, 37 ' executed, of which four to twenty are arranged one behind the other in the circumferential direction.
  • the arc shape of the guide elements 37, 37 'in one and the same direction ensures that a fluid flowing between them is subjected to a swirl.
  • Exemplary embodiments have a constant axial height over their entire arc length, while the guide elements 37 'in FIG. 4 have contours which are distinguished by upper boundary sides 38 which drop radially from the outside inwards towards the outlet opening 22.
  • the drop in the axial extent of the guide elements 37 'inwards towards the longitudinal axis 2 of the valve can, for. B. linear or exponential.
  • two main flows are generated downstream of the valve seat surface 29 in the fluid entering the opening area 35 in the form of a ring.
  • the ways of forming the two flow components 33 and 34 are identified in FIG. 3.
  • the flow component 33 arises from the fact that part of the fluid immediately downstream of the valve closing body 7 does not get between the lower guide elements 37, 37 ', but above that Guide elements 37, 37 'and thus without swirling flows in the direction of the inner outlet opening 22 and enters it.
  • Another part of the fluid flows into the areas between the guide elements 37, 37 ', where it is subjected to a swirl and thus the swirled flow component 34 is formed, which encases the inner flow component 33.
  • the guide elements 37, 37 ' are, for example, formed in one piece on the perforated disk 21, wherein particularly known methods of electroforming (LIGA, MIGA technology) are suitable for the production. Widths of approximately 20 to 50 ⁇ m and axial heights of approximately 100 to 300 ⁇ m are conceivable orders of magnitude for the guide elements 37, 37 '. These sizes are only for better understanding and do not limit the invention in any way.
  • the swirl-generating means 23 shown in FIGS. 6 to 8 are, for. B. to twist attachments made separately from the perforated disc 21
  • the z. B. are firmly connected to the perforated disk 21 by means of gluing, welding or soldering.
  • the swirl attachments 40 can also be provided in one piece on the perforated disk 21. Similar to the guide elements 37, 37 ', the swirl attachments 40 also protrude into the opening area 35 of the
  • the swirl attachments 40 represent components which are distinguished by two axially successive layers 41 and 42.
  • Each layer 41, 42 serves as the functional level for generating a swirled flow.
  • the upper layer 41 facing the valve closing body 7 has a smaller outer diameter than the lower layer 42 facing the outlet opening 22. Starting from the outer radial circumference, each layer extends
  • the inner flow area 55 is designed as stepped as the outer contour of the swirl attachment 40, ie in the upper layer 41 the flow area 55 has a smaller diameter than in the lower layer 42.
  • the swirl channels 51, 52 are e.g. B. provided with square or circular cross sections.
  • the swirl cap 40 is closed towards the valve closing body 7 by an upper boundary surface 56, but is of course open towards the outlet opening 22.
  • FIG. 7 is a sectional illustration along the line VII-VII in FIG. 6 through the upper layer 41 of the swirl attachment 40. From FIG. 7 it can be seen that the swirl channels 51, 52 which open tangentially into the flow region 55 have an opposite orientation, so that a fluid flowing in receives two largely radially separate, swirling, opposite flow components 33, 34. In the outlet opening 22, this flow distribution generated in the flow area 55 is largely retained, so that the increased shear forces occurring in the border areas of the two flow components 33, 34 lead to turbulence, which is particularly desirable for improved atomization of the fluid.
  • FIG. 8 An exemplary embodiment of a swirl attachment 40 is shown in FIG. 8, which differs only slightly from the swirl attachment 40 shown in FIG.
  • this swirl attachment 40 an axially extending central pin 58 is provided which, starting from the boundary surface 56, extends centrally through the flow region 55 into the outlet opening 22.
  • the pin 58 is, for example, made in one piece on the swirl attachment 40 or is connected to the swirl attachment 40 by welding, soldering or gluing.
  • this design of the swirl attachment 40 can be very well lamella-like beam paths z. B. in the form of a hollow cone.
  • the arrangement according to FIG. 6 tends to generate beam profiles in the form of full cones.
  • FIG. 9 shows a schematically illustrated, idealized speed distribution radially over the diameter of the outlet opening 22 downstream of the swirl attachment 40 in FIG. 6, from which the opposing flow components 33 and 34 emerge very well.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

La soupape selon l'invention présente, en aval d'un siège de soupape (29), des moyens générateurs de tourbillons (23), configurés de façon à produire au moins deux courants de fluide à injecter, ces courants s'écoulant de façon décalée radialement l'un par rapport à l'autre et présentent des directions d'écoulement divergentes. Aux zones limites des composants d'écoulement présentant des directions différentes, il se produit des forces de cisaillement dues aux tourbillons et engendrant des turbulences. Ce dispositif permet d'obtenir, sans apport d'énergie supplémentaire, une pulvérisation uniforme extrêmement fine du fluide, en particulier d'un carburant. La soupape convient notamment pour l'utilisation dans des systèmes d'injection de carburant dans des moteurs à combustion interne à compression du mélange, à allumage extérieur.
EP97942763A 1996-09-12 1997-08-30 Soupape, en particulier soupape d'injection de carburant Expired - Lifetime EP0859910B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19637103A DE19637103A1 (de) 1996-09-12 1996-09-12 Ventil, insbesondere Brennstoffeinspritzventil
DE19637103 1996-09-12
PCT/DE1997/001905 WO1998011341A1 (fr) 1996-09-12 1997-08-30 Soupape, en particulier soupape d'injection de carburant

Publications (2)

Publication Number Publication Date
EP0859910A1 true EP0859910A1 (fr) 1998-08-26
EP0859910B1 EP0859910B1 (fr) 2002-03-20

Family

ID=7805392

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97942763A Expired - Lifetime EP0859910B1 (fr) 1996-09-12 1997-08-30 Soupape, en particulier soupape d'injection de carburant

Country Status (5)

Country Link
US (1) US6089473A (fr)
EP (1) EP0859910B1 (fr)
JP (1) JP2000500213A (fr)
DE (2) DE19637103A1 (fr)
WO (1) WO1998011341A1 (fr)

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DE19815780A1 (de) * 1998-04-08 1999-10-14 Bosch Gmbh Robert Brennstoffeinspritzventil und Verfahren zur Montage eines Brennstoffeinspritzventils
DE19815795A1 (de) * 1998-04-08 1999-10-14 Bosch Gmbh Robert Zerstäuberscheibe und Brennstoffeinspritzventil mit Zerstäuberscheibe
DE19815800A1 (de) 1998-04-08 1999-10-14 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10038098A1 (de) * 2000-08-04 2002-02-14 Bosch Gmbh Robert Brennstoffeinspritzventil
US6390067B1 (en) * 2000-08-10 2002-05-21 Delphi Technologies, Inc. Valve seat retainer for a fuel injector
DE10041440A1 (de) 2000-08-23 2002-03-07 Bosch Gmbh Robert Drallscheibe und Brennstoffeinspritzventil mit Drallscheibe
DE10046304C1 (de) * 2000-09-19 2002-06-06 Bosch Gmbh Robert Verfahren zum Herstellen eines Ventilsitzkörpers eines Brennstoffeinspritzventils
DE10056006A1 (de) 2000-11-11 2002-05-16 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10061571B4 (de) * 2000-12-11 2007-03-22 Robert Bosch Gmbh Brennstoffeinspritzventil
US6513730B1 (en) 2001-03-21 2003-02-04 The United States Of America As Represented By The National Aeronautics And Space Administration MEMS-based spinning nozzle
US6848635B2 (en) * 2002-01-31 2005-02-01 Visteon Global Technologies, Inc. Fuel injector nozzle assembly with induced turbulence
DE10229871A1 (de) * 2002-07-03 2004-01-15 Robert Bosch Gmbh Zerstäubungsanordnung
US6938839B2 (en) * 2002-08-15 2005-09-06 Visteon Global Technologies, Inc. Needle alignment fuel injector
JP4154317B2 (ja) * 2003-04-25 2008-09-24 トヨタ自動車株式会社 燃料噴射弁
US7469845B2 (en) * 2003-10-27 2008-12-30 Continental Automotive Systems Us, Inc. Fluidic flow controller orifice disc for fuel injector
ITTO20030990A1 (it) * 2003-12-10 2005-06-11 Fiat Ricerche Dispositivo iniettore di combustibile per un motore a combustione interna.
JP2005226846A (ja) * 2004-02-10 2005-08-25 Daikin Ind Ltd 膨張弁及び冷凍装置
JP5978154B2 (ja) * 2013-03-08 2016-08-24 日立オートモティブシステムズ株式会社 燃料噴射弁
JP5887291B2 (ja) * 2013-03-08 2016-03-16 日立オートモティブシステムズ株式会社 燃料噴射弁
JP6429461B2 (ja) * 2013-05-13 2018-11-28 株式会社エンプラス 燃料噴射装置用ノズルプレート
CN105986863A (zh) * 2015-02-15 2016-10-05 浙江福爱电子有限公司 一种排气后处理用旋流喷嘴
WO2018053012A1 (fr) * 2016-09-13 2018-03-22 Spectrum Brands, Inc. Moteur de pomme de douche à pot de turbulence

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Also Published As

Publication number Publication date
US6089473A (en) 2000-07-18
DE59706677D1 (de) 2002-04-25
EP0859910B1 (fr) 2002-03-20
DE19637103A1 (de) 1998-03-19
JP2000500213A (ja) 2000-01-11
WO1998011341A1 (fr) 1998-03-19

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