EP1129287A1 - Buse d'injection pour moteurs a combustion interne avec pointeau pourvu d'une rainure annulaire - Google Patents

Buse d'injection pour moteurs a combustion interne avec pointeau pourvu d'une rainure annulaire

Info

Publication number
EP1129287A1
EP1129287A1 EP00965779A EP00965779A EP1129287A1 EP 1129287 A1 EP1129287 A1 EP 1129287A1 EP 00965779 A EP00965779 A EP 00965779A EP 00965779 A EP00965779 A EP 00965779A EP 1129287 A1 EP1129287 A1 EP 1129287A1
Authority
EP
European Patent Office
Prior art keywords
nozzle
injection nozzle
nozzle needle
annular groove
injection
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
EP00965779A
Other languages
German (de)
English (en)
Other versions
EP1129287B1 (fr
Inventor
Friedrich Boecking
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 EP1129287A1 publication Critical patent/EP1129287A1/fr
Application granted granted Critical
Publication of EP1129287B1 publication Critical patent/EP1129287B1/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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • 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
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal

Definitions

  • the invention is based on an injection nozzle for internal combustion engines with at least one spray hole, with a nozzle needle seat and with a nozzle needle.
  • Injection nozzles of the generic type have a large scatter in the flow resistance and thus also in the amount of fuel injected, especially in the partial stroke area of the nozzle needle. As a result, the emission and consumption behavior of many of the internal combustion engines equipped with these injection nozzles is not optimal.
  • an injection nozzle for Internal combustion engines with at least one spray hole, with a nozzle needle seat and with a nozzle needle, the end of the nozzle needle facing the nozzle needle seat having an annular groove.
  • the annular groove in the end of the nozzle needle facing the nozzle needle seat is decisive for the throttling action of the injection nozzle in the partial stroke area of the nozzle needle. Since it is possible to produce ring grooves with a high degree of repeatability, the throttling effect of the injection nozzle between different examples of an injection nozzle of the same type thus diffuses only to a very limited extent. For this reason, by measuring the operating behavior of an injection nozzle according to the invention, the operating behavior of all other identical injection nozzles can be predicted with much greater accuracy and the control of the injection process can be optimized accordingly.
  • a variant of an injection nozzle according to the invention provides that the nozzle needle seat is frustoconical, which results in a good sealing effect and good centering of the nozzle needle in the nozzle needle seat.
  • the cone angle of the nozzle needle seat is 60 °, so that a good one
  • the end of the nozzle needle facing the nozzle needle seat is a cone and is the
  • Cone angle of the nozzle needle up to one degree, preferably 15-30 minutes, greater than the cone angle of the nozzle needle seat, so that the sealing surface is reduced and moved into the area of the largest diameter of the nozzle needle.
  • the annular groove runs parallel to the base of the cone, so that the same flow conditions prevail over the entire circumference of the nozzle needle.
  • a blind hole adjoins the nozzle needle seat, which has at least one spray hole, so that the advantages of the nozzle needle according to the invention can also be used with blind hole injection nozzles.
  • the distance of the transition between the blind hole and the nozzle needle seat from the base of the injection nozzle and the distance of the annular groove from the base of the injection nozzle are essentially the same, so that the annular groove instead of the transition in the partial stroke area of the nozzle needle Throttle effect of the injector is determined.
  • Width of the annular groove is 0.1 mm to 0.3 mm, preferably 0.16 mm to 0.24 mm, so that the annular groove is decisive for the throttling effect of the injection nozzle over a sufficiently large partial stroke range.
  • the ring groove must be so large that only the front edge of the ring groove throttles for a short time.
  • the depth of the annular groove is 0.02 mm to 0.2 mm, preferably 0.08 mm to 0.14 mm, so that the
  • the blind hole is conical, so that the part-load behavior of conical blind-hole injection nozzles is improved.
  • the blind hole is cylindrical, so that the partial load behavior of cylindrical blind hole injection nozzles is also improved.
  • blind hole is a mini blind hole or a micro blind hole, so that the advantages according to the invention can also be used with these injection nozzles.
  • a variant according to the invention provides that the nozzle needle seat has at least one spray hole, so that the advantages of the nozzle needle according to the invention can also be used with seat hole injection nozzles.
  • the problem with seat hole injection nozzles also sometimes arises that, due to the magical centering of the nozzle needle with respect to the nozzle needle seat, the pressure of the fuel applied to the spray holes distributed over the circumference is not the same, which can lead to unfavorable conditions during the injection.
  • the annular groove allows pressure equalization between the spray holes, so that the poor centering of the nozzle needle does not have a negative effect on the injection conditions.
  • the depth of the ring groove is smaller than the width of the ring groove or that the depth of the ring groove is 0.02 mm to 0.1 mm, preferably 0.04 mm to 0.07 mm, so that the volume of the annular groove remains small and the annular groove nevertheless has a sufficient influence on the throttling effect of the injection nozzle.
  • FIG. 2 a characteristic curve of the hydraulic diameter of a blind hole injection nozzle according to the invention over the stroke of the nozzle needle;
  • Figure 3 shows a cross section through an inventive
  • an injection nozzle 1 is shown with a conical blind hole 2.
  • the blind hole 2 can also be cylindrical or it can be a mini or Act micro blind hole 2. In the latter, the volume of the blind hole 2 is reduced compared to the type shown in FIG. 1. As a result, less fuel evaporates into the combustion chamber when the internal combustion engine is switched off.
  • the fuel not shown, reaches the combustion chamber, which is also not shown, from the blind hole 2 via a spray hole 3.
  • a frustoconical nozzle needle seat 4 At the conical blind hole 2 is a frustoconical nozzle needle seat 4.
  • the nozzle needle seat 4 can have a cone angle of 60 °.
  • a nozzle needle 5 rests on the nozzle needle seat 4. It can be clearly seen in FIG. 1 that the cone angle of the nozzle needle 5 is greater than the cone angle of the nozzle needle seat 4. As a result, the contact zone 6 between the nozzle needle 5 and the nozzle needle seat 4 lies in the region of the largest diameter of the nozzle needle 5 and the surface pressure between the nozzle needle 5 and the nozzle needle seat 4 is increased. The difference between the cone angles of the nozzle needle 5 and nozzle needle seat 4 is exaggerated in FIG. 1. As a rule, the above-mentioned Difference less than 1 degree and moves in the range of a few minutes of angle.
  • the transition between blind hole 2 and nozzle needle seat 4 according to the prior art is an edge 7 which arises when the nozzle needle seat 4 is ground.
  • the edge 7 can be a sharp burr or a smooth edge.
  • the flow resistance of the edge 7 is significantly influenced by the nature thereof.
  • An annular groove 8 inserted or ground into the nozzle needle 5 reduces the influence of the edge 7 on the
  • the distance of the The annular groove 8 from a base 9 of the injection nozzle 1 is approximately the same size as the distance from the base 9 of the injection nozzle 1 and the edge 7.
  • the throttling effect of the injection nozzle 1 is not, or at least not appreciably, different from that Geometry of edge 7 influenced.
  • This effect is based on the fact that, owing to the large hydraulic diameter of the annular gap between the annular groove 8 and the edge 7 compared to the annular gap between the nozzle needle seat 4 and the cone of the nozzle needle 5, the flow resistance in the latter annular gap is lower than that of the former annular gap. Since both flow resistances are connected in series, the smallest individual resistance is essentially decisive for the flow resistance of the entire injector.
  • FIG. 2 the hydraulic diameter 11 of a blind hole injection nozzle 1 is plotted qualitatively over the nozzle needle stroke 10.
  • the hydraulic diameter 11 is a size by means of which any cross-sections through which flow can be made are comparable with regard to their flow resistance. The serves as a reference
  • the nozzle needle stroke 10 was divided into two areas. A first area extends from zero to "a”, the second area, hereinafter referred to as partial stroke area, extends from “a” to "b”. At “c” the full nozzle needle stroke is reached. If a closed injection nozzle 1, in which the nozzle needle 5 rests on the nozzle needle seat 4, is opened, there is a very small gap in the region of the contact zone 6 with a very small nozzle needle stroke 10, through which the fuel under pressure can flow into the blind hole 2 , This very narrow gap decisively determines the flow resistance of the injection nozzle 1 and thus also defines the hydraulic diameter 11. Since the flow resistance of this very narrow gap is large, the hydraulic diameter 11 of the injection nozzle 1 is very small with a very small nozzle needle stroke 10.
  • the flow resistance of injection nozzles 1 is largely determined by the edge 7 between nozzle needle seat 4 and blind hole 2.
  • the edge 7 in the partial stroke range is thus also of great importance for the hydraulic diameter of the injection nozzle 1. This means that changes in the geometry of the edge 7 result in changes in the hydraulic diameter 11.
  • the spray hole 3 of the injection nozzle 1 is decisive for the hydraulic diameter of the injection nozzle 1.
  • FIG. 2 shows characteristic curves 12 and 13 of an injection nozzle 1 according to the prior art and a characteristic curve 14 of a blind hole injection nozzle 1 according to the invention.
  • the nozzle needle 5 has no annular groove. Because of the strains in the geometry of the edge 7 described above, the characteristics of different specimens also scatter identical injection nozzles 1, in particular in the partial stroke range. This is illustrated by the deviations of the characteristic curves 12 and 13 from one another in FIG. 2.
  • the characteristic curve 14 represents an injection nozzle according to the invention in which the throttling effect of the edge 7 does not come into play, particularly in the partial stroke range, since the fuel can escape into the annular groove 8.
  • the hydraulic diameter 11 of the injection nozzle 1 according to the invention is larger in the partial stroke area than that of injection nozzles 1 according to the prior art.
  • the characteristic curves 14 of different types of injection nozzles 1 of the same type according to the invention scatter much less, in particular in the partial stroke range, since the geometry of the annular groove 8 can be produced with great repeatability.
  • the map of the internal combustion engine and the associated injection system is determined by measurements using one or more selected test copies.
  • the characteristic maps determined in this way are used as a basis for all injection systems of the same type.
  • the characteristic curve 12 is a measured characteristic curve and that this characteristic curve 12 is stored in the control unit of the injection system. It is further assumed that an injection nozzle 1 taken from series production has the characteristic curve 13. If the injection nozzle 1 with the characteristic curve 13 interacts with a control unit in which the characteristic curve 12 is stored, then the actual injection quantity in the partial stroke area of the injection nozzle 1 with the characteristic curve 13 does not match the optimal injection tightness measured in the test specimens according to the characteristic curve 12 match, so that the performance and / or emission behavior of the Internal combustion engine is deteriorating.
  • the characteristic curves 14 scatter only to a very small extent, so that in all of the nozzles 1 equipped with the invention
  • the correspondence between the characteristic curve 14 stored in the control unit and the characteristic curves 14 of the built-in injection nozzles 1 is significantly improved.
  • the correspondence can be improved, for example by a factor of 2 to 3, compared to the scatter in the case of injection nozzles 1 according to the prior art.
  • the quantity of fuel actually injected corresponds exactly to the injection quantity specified by the control unit, and the consumption and emission behavior of the internal combustion engine is optimal.
  • FIG. 3 shows an injection nozzle 1 according to the invention with spray holes 3 designed as seat holes.
  • the reference numbers correspond to those used in FIG. 1. The main difference is that in
  • the ring groove 8 according to the invention is arranged in the case of seat hole injection nozzles at the level of the spray holes 3, so that the

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

L'invention concerne une buse d'injection (1) dont le pointeau (5) présente une rainure annulaire (8) dans la zone de transition (7) entre le trou borgne (2) et le siège de pointeau (4). Dans les buses d'injection à trou(s) borgne(s), la rainure annulaire (8) se trouve dans la zone du ou des trou(s) borgne(s) (3). Grâce à cette rainure annulaire (8), la tolérance de la résistance à l'écoulement de la buse d'injection (1), lors de la levée partielle du pointeau (5), est réduite et cela permet un dosage plus précis du carburant injecté.
EP00965779A 1999-09-04 2000-08-18 Buse d'injection pour moteurs a combustion interne avec pointeau pourvu d'une rainure annulaire Expired - Lifetime EP1129287B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19942370A DE19942370A1 (de) 1999-09-04 1999-09-04 Einspritzdüse für Brennkraftmaschinen mit einer Ringnut in der Düsennadel
DE19942370 1999-09-04
PCT/DE2000/002814 WO2001018387A1 (fr) 1999-09-04 2000-08-18 Buse d'injection pour moteurs a combustion interne avec pointeau pourvu d'une rainure annulaire

Publications (2)

Publication Number Publication Date
EP1129287A1 true EP1129287A1 (fr) 2001-09-05
EP1129287B1 EP1129287B1 (fr) 2005-05-18

Family

ID=7920896

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00965779A Expired - Lifetime EP1129287B1 (fr) 1999-09-04 2000-08-18 Buse d'injection pour moteurs a combustion interne avec pointeau pourvu d'une rainure annulaire

Country Status (6)

Country Link
US (1) US7128280B1 (fr)
EP (1) EP1129287B1 (fr)
JP (1) JP4709451B2 (fr)
KR (1) KR100737712B1 (fr)
DE (2) DE19942370A1 (fr)
WO (1) WO2001018387A1 (fr)

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DE10031264A1 (de) 2000-06-27 2002-01-17 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10163908A1 (de) 2001-12-22 2003-07-03 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10246693A1 (de) * 2002-10-07 2004-04-15 Siemens Ag Einspritzvorrichtung zum Einspritzen von Kraftstoff
DE10247958A1 (de) * 2002-10-15 2004-04-29 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine
DE10253721A1 (de) * 2002-11-19 2004-06-03 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10304135A1 (de) * 2003-02-03 2004-08-05 Robert Bosch Gmbh Einspritzdüse
DE602004014854D1 (de) * 2003-07-15 2008-08-21 Delphi Tech Inc Einspritzventil
DE102005025135A1 (de) * 2005-06-01 2006-12-07 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
US7578450B2 (en) * 2005-08-25 2009-08-25 Caterpillar Inc. Fuel injector with grooved check member
US7360722B2 (en) * 2005-08-25 2008-04-22 Caterpillar Inc. Fuel injector with grooved check member
JP5044556B2 (ja) * 2005-08-25 2012-10-10 キャタピラー インコーポレイテッド 溝付逆止部材を備えた燃料噴射器
DE102006012242A1 (de) * 2006-03-15 2007-09-20 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
JP2009138614A (ja) * 2007-12-05 2009-06-25 Mitsubishi Heavy Ind Ltd 蓄圧式燃料噴射装置の燃料噴射弁
EP2369166B1 (fr) * 2010-03-22 2017-12-13 Delphi International Operations Luxembourg S.à r.l. Buse à injection
WO2012085901A2 (fr) * 2011-05-09 2012-06-28 Lietuvietis Vilis I Canal d'égalisation de pression à trous recouverts par aiguille
JP2014194197A (ja) * 2013-03-29 2014-10-09 Denso Corp 燃料噴射ノズル
JP5976586B2 (ja) * 2013-03-29 2016-08-23 株式会社デンソー 燃料噴射ノズル
DE102013217371A1 (de) * 2013-08-30 2015-03-05 Robert Bosch Gmbh Kraftstoffinjektor
DE102019210631A1 (de) * 2019-07-18 2021-01-21 Robert Bosch Gmbh Kraftstoffinjektor für Brennkraftmaschinen
US20230374961A1 (en) * 2022-05-20 2023-11-23 Caterpillar Inc. Fuel injector nozzle assembly including needle having flow guiding tip for directing fuel flow

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Also Published As

Publication number Publication date
US7128280B1 (en) 2006-10-31
JP4709451B2 (ja) 2011-06-22
DE50010346D1 (de) 2005-06-23
DE19942370A1 (de) 2001-03-22
KR100737712B1 (ko) 2007-07-11
EP1129287B1 (fr) 2005-05-18
WO2001018387A1 (fr) 2001-03-15
KR20010092436A (ko) 2001-10-24
JP2003508684A (ja) 2003-03-04

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